EP0627552B1 - Kraftstoffeinspritzpumpe - Google Patents
Kraftstoffeinspritzpumpe Download PDFInfo
- Publication number
- EP0627552B1 EP0627552B1 EP94103494A EP94103494A EP0627552B1 EP 0627552 B1 EP0627552 B1 EP 0627552B1 EP 94103494 A EP94103494 A EP 94103494A EP 94103494 A EP94103494 A EP 94103494A EP 0627552 B1 EP0627552 B1 EP 0627552B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- pump
- working space
- fuel injection
- delivery stroke
- 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
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
- F02D1/16—Adjustment of injection timing
- F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
- F02D1/183—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
- F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
- F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
- F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
- F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
- F02M41/128—Varying injection timing by angular adjustment of the face-cam or the rollers support
Definitions
- the invention relates to a fuel injection pump according to the Genus of claim 1.
- a fuel injection pump is already known from DE-A-29 23 445.
- the problem with fuel injection pumps is as follows: If the Delivery rate of the fuel injection pump at the nominal output point the internal combustion engine at maximum load and maximum speed optimized so that there the maximum permissible pressure in the pump work space the fuel injection pump occurs, then this pressure is in usually at low speed of the fuel injection pump or the associated internal combustion engine in the lower full load point for the Quality of the fuel input into the combustion chambers of the internal combustion engine too low due to injectors. If you raise the funding rate in this area, then the pressure rises as desired this lower full load point, but at the nominal power point the Fuel injection pump overloaded. So there has to be an increase of the pressure in the lower full load point to ensure that the Pump is not overloaded at the nominal output point.
- features of claim 1 have the advantage that the pressure in the pump workspace in the low speed load range reaches a desired high injection pressure without high Speed load range of the fuel injection pump this too high pressure is overloaded.
- An advantageous embodiment of the invention consists in the configuration the fuel injection pump according to claim 4, wherein in from a certain load speed point, the delivery rate is simple of the pump piston is delayed over a certain range of rotation angles becomes.
- This gives an injection pressure curve shape, the controlled by the pressure in the pump work space or by this generated pressure in the working area controlled in front of the adjusting piston becomes.
- the relief valve can also be used serve as a removal device by starting from or after of the high-pressure delivery stroke of the pump piston at least temporarily is opened.
- the control of this valve can be advantageous This is done by a sensor that detects the pressure in the pump work space be controlled or by an injection duration control, which itself has an indirect effect on the pressure in the pump work area.
- the pressure in the work area before the adjusting piston according to claim 10 by a electrically controlled valve controlled according to claim 11 clocked is controlled so that its opening time in essentially complementary to the opening times of the relief valve lies.
- FIG. 1 shows a first embodiment of the control device separate escape piston
- Figure 2 a related to Figure 1 Diagram of the cam stroke over the angle of rotation
- Figure 3 is a diagram the injection course over the angle of rotation
- Figure 4 shows a second Version with two check valves
- Figure 5 shows a third version with a drain check valve and an additional one 2/2-way solenoid valve
- Figure 6 is related to Figure 5 Diagram of the cam stroke at the work of the control valve and additional solenoid valve
- Figure 7 shows a fourth embodiment with an additional 2/2-way solenoid valve and Figure 8 one on the Figure 7 related diagram of the cam stroke and the element pressure when working the control valve and the additional solenoid valve.
- FIG. 1 shows a cylinder 1 in which an adjusting piston 2 is movable against the force of a spring 3.
- the adjusting piston 2 has a recess 4 into which a free end 5 of a bolt 6 intervenes.
- One of the spring 3 opposite working space 7 of the Cylinder 1 is connected via a line 8 to an additional cylinder 9 namely at its working chamber 10.
- an additional cylinder 9 is an evasive piston 11 is arranged, the working chamber 10 as movable wall limited.
- Stop 14 used, the path of the evasive piston 11 on a limited stroke (AW).
- AW limited stroke
- On line 8 are one Pressure medium inflow line 15, which is increased by a pressure medium Pressure leading pressure medium source 37 discharges and a pressure medium drain line 16, which leads to a relief room, connected.
- a pressure medium inflow line 15 In the pressure medium inflow line 15 is an inflow check valve 17 with a throttle 19 and in the pressure medium discharge line 16 an electrically controlled valve, here a solenoid valve 18, is arranged, that serves to regulate the pressure in the work area.
- the adjusting piston 2 is the one used in fuel injection pumps known pistons of an injection start adjustment device. Adjusted according to the displacement of the adjusting piston the bolt 6 as the corresponding bolt in one by the DE-A-21 58 689 known fuel injection pump one in this Registration not shown roller ring, but rotatable except for the Rotation by the pin 6 stationary in the housing of the fuel injection pump is stored and on its rollers a cam expires with their cams.
- the cam disc is included a drive shaft of the fuel injection pump and coupled to another with a pump piston, which due to the rotation of the Drive shaft rotating together with the cam disc Performs movement while serving as a distributor and at the same time due to the cam disc running on the rollers back and forth Performing movement and suction and as a pump piston Carrying out strokes.
- the pump piston closes as usual known, but not shown here, a pump work room one that is filled with fuel during the suction stroke and during the delivery stroke Fuel under high pressure to one injector on each Promotes internal combustion engine.
- the injectors are essentially the beginning of the Stroke movement of the cam disc together with the pump piston the course of which determines the roles of the roller ring and that End of delivery, to determine the fuel injection quantity by opening a relief channel.
- the cam disc is replaced by a resetting Force in the form of return springs on the roller ring held. This restoring force is also due to the reaction force of the pump piston during its delivery stroke.
- the roller ring experiences via the flank of the cams of the cam disc a force in its circumferential direction, which force is the actuating force counteracts the adjusting piston.
- the degree of this pressure increase corresponds to the pressure generated in the pump work space.
- the pressure increase on the other hand is only possible because the check valve 17, that to the pressure medium source closes that supplied to the work area Pressure medium volume with closed solenoid valve includes.
- the bias of the spring 12 so chosen that in an upper range of the achievable pressure in Pump work area uses the evasive movement of the evasive piston and thus prevents excessive pressure in the pump work space arises. Because of the throttling effects in the high pressure side Line system is in a known manner at low speed lower delivery rate with a lower final maximum pressure in Pump workspace achieved and a high at high speed Delivery rate with a correspondingly higher final maximum pressure in Pump work room. This high one that arises at high speed Ultimate maximum pressure is now with the device according to the invention Helped by the evasive piston 12. This effect is special Particularly pronounced even at full load, since the attainable one Ultimate maximum pressure depends on the high pressure displacement of the Pump piston. At full load, the final maximum pressure reached is greater than at partial load.
- the stop 14 comes into play.
- the Preload of the preloaded spring 12 is designed to be lower, so the escape piston 11 already at a lower pressure in the pump work space start at a lower injection rate to dodge.
- the injection rate would then range according to the injection curve display with escape piston 11 (AWK) of the diagram in FIG. 3 over the angle of rotation ⁇ with a smaller slope until the Dodge piston comes to rest on the stop 14.
- ANK injection curve display with escape piston 11
- FIGS. 5 and 6 A solution that is improved in comparison is shown in FIGS. 5 and 6 shown.
- Deviating from the design according to Figure 4 is here in addition to the solenoid valve 18 and instead of the check valve 17 with a throttle a further 2/2 solenoid valve 34 in the pressure medium supply line 15 have been used.
- the additional solenoid valve 34 enables fast over a large opening cross-section Refill the amount of liquid escaped via the check valve 33.
- the two solenoid valves 18 and 34 switched so that the control of the inflow and outflow in the suction stroke phase of the pump piston.
- Figure 6 shows the assignment of the solenoid valve opening phases of the Solenoid valve 34 (MV 34) and the solenoid valve 18 (MV 18) in relation to the cam elevation curve via the angle of rotation ⁇ .
- the solenoid valves 34 and 18 are driven in opposite directions in such a way that for a pressure increase in the working space 7, the solenoid valve 18 a is open for a shorter time than the solenoid valve 34.
- the solenoid valves can also be controlled complementarily with one another variable duty cycle, with the variation of the duty cycle the opening time of one valve at the expense of the other Valve is changed.
- the pressure medium inflow line 15 is again the 2/2 solenoid valve 34 and in the pressure medium drain line 16 the 2/2-solenoid valve 18.
- a pressure sensor 35 is provided, which is symbolically in the drawing in Figure 7 is connected to the line 8 and on the other hand in connection with a control device, not shown stands, depending on how, depending on operating parameters also the solenoid valves 18 in the exemplary embodiment according to FIG. 5 and 34 can be controlled to the desired pressure in the work space 7 to control the start of funding.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
- High-Pressure Fuel Injection Pump Control (AREA)
Description
Claims (11)
- Kraftstoffeinspritzpumpe für Brennkraftmaschinen mit einem von einem Nockenantrieb angetriebenen Pumpenkolben, der in einem Pumpenzylinder einen Pumpenarbeitsraum einschließt, aus dem beim Förderhub des Pumpenkolbens Kraftstoff unter Hochdruck zu einem Kraftstoffeinspritzventil gefördert wird, wobei der Nockenantrieb einen im wesentlichen feststehenden Teil und einen von einer Antriebswelle der Einspritzpumpe angetriebenen bewegten Teil aufweist, von denen einer mit einer Nockenbahn versehen ist und von denen der bewegte Teil der Nockenbahn folgend zugleich den Pumpenkolben bewegt durch den über die Nockenbahn eine rücktreibende Kraft auf den im wesentlichen feststehenden Teil ausgeübt wird und mit einem Verstellkolben (2), der in einem Zylinder (1) einen Arbeitsraum (7) einschließt, welcher mit Druckmittel aus einer Druckmittelquelle versorgt wird und durch das Druckmittel entgegen einer Rückstellkraft (3) verstellbar mit dem im wesentlichen feststehenden Teil des Nockenantriebs gekoppelt ist, wobei die rücktreibende Kraft der Rückstellkraft gleichgerichtet ist und mit seiner Verstellung den Hochdruckförderhubbeginn des Pumpenkolbens in Bezug auf eine Drehstellung der Antriebswelle verstellt, und der Druckmitteldruck im Arbeitsraum (7) zur Veränderung des Förderhubbeginns in Abhängigkeit von Betriebsparametern der Brennkraftmaschine gesteuert wird und mit einer Entnahmevorrichtung zur gesteuerten Entnahme von Druckmittelmengen aus dem Arbeitsraum (7) während des Hochdruckförderhubs des Pumpenkolbens, wobei der Arbeitsraum (7) eine ein Steuerorgan (17,34) enthaltende, von der Druckmittelquelle herführende Druckmittelzuführleitung (15) und eine ein elektrisch gesteuertes Entlastungsventil (18) aufweisende Druckmittelabflußleitung (16) zu einem Entlastungsraum hat, durch das der Druck im Arbeitsraum (7) zur Veränderung des jeweiligen Förderhubbeginns so gesteuert wird, daß dieser jeweils vor dem Förderhubbeginn eines jeden Pumpenkolbenförderhubs eingestellt ist, dadurch gekennzeichnet, daß die Entnahme von Druckmittelmengen durch die Entnahmevorrichtung in Abhängigkeit vom Druck im Arbeitsraum oder vom diesen während des Hochdruckförderhubs beeinflussenden Druck im Pumpenarbeitsraum gesteuert wird.
- Kraftstoffeinspritzpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Entnahmevorrichtung aus einem ständig mit dem Arbeitsraum (7) in Verbindung stehenden Druckhalteventil (33) besteht, durch dessen Öffnungsdruck der Druckverlauf im Arbeitsraum (7) oder im Pumpenarbeitsraum während des Hochdruckförderhubs des Pumpenkolbens bestimmt ist.
- Kraftstoffeinspritzpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Entnahmeeinrichtung eine bewegliche Wand (11) aufweist, die hydraulisch an den Arbeitsraum (7) angrenzt und auf ihrer Rückseite von eine vorgespannten Feder (12) beaufschlagt ist, die so eingestellt ist, daß die bewegliche Wand ab einem bestimmten Druck im Arbeitsraum oder Pumpenarbeitsraum verstellt wird.
- Kraftstoffeinspritzpumpe nach Anspruch 3, dadurch gekennzeichnet, daß auf der Rückseite der beweglichen Wand (11) ein Wegbegrenzungsanschlag (14) für die Bewegung der beweglichen Wand entgegen der Kraft der vorgespannten Feder (12) vorgesehen ist und der bestimmte Druck im mittleren Bereich des durch den Pumpenkolben über den Betriebsbereich der Krafstoffeinspritzpumpe während seines jeweiligen Förderhubes erreichbaren Druck liegt.
- Kraftstoffeinspritzpumpe nach Anspruch 3 bis 4, dadurch gekennzeichnet, daß die vorgespannte Feder sich ortsfest am Pumpengehäuse abstützt
- Kraftstoffeinspritzpumpe nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß das Steuerorgan in der Druckmittelzuflußleitung (15) ein Rückschlagventil (17) ist, das in Richtung Arbeitsraum öffnet.
- Kraftstoffeinspritzpumpe nach Anspruch 1, dadurch gekennzeichnet, daß das Entlastungsventil (18) als Entnahmevorrichtung dient und in Abhängingkeit von Betriebsparametern während wenigstens eines Teils des Förderhubs des Pumpenkolbens geöffnet ist.
- Kraftstoffeinspritzpumpe nach Anspruch 7, dadurch gekennzeichnet, daß das Entlastungsventil (18) in Abhängigkeit vom erreichten Druck im Pumpenarbeitsraum ab Überschreiten eines vorgegebenen Drucks geöffnet wird.
- Kraftstoffeinspritzpumpe nach Anspruch 7, dadurch gekennzeichet, daß das Entlastungsventil (18) von einer Einspritzdauerregelung gesteuert wird, wobei die Einspritzdauer von einem die Öffnungsdauer eines von der Einspritzpumpe versorgten Einspritzventil erfassenden Sensors gemessen wird.
- Kraftstoffeinsritzpumpe nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, daß das Steuerorgan in der Druckmittelzuflußleitung ein elektrisch gesteuertes Zuflußventil (34) ist.
- Kraftstoffeinspritzpumpe nach Anspruch 10, dadurch gekennzeichnet, daß das Entlastungsventil (18) und das Zuflußventil (34) zwischen den Betriebszeiten, in denen der Pumpenkolben seinen Förderhub ausführt vorzugweise mit variablen Tastverhältnis getaktet angesteuert wird zu Veränderung des die Einstellung des jeweils gewünschten Förderhubbeginns steuernden Druckes im Arbeitsraum (7).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4311672 | 1993-04-08 | ||
DE4311672A DE4311672A1 (de) | 1993-04-08 | 1993-04-08 | Kraftstoffeinspritzpumpe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0627552A1 EP0627552A1 (de) | 1994-12-07 |
EP0627552B1 true EP0627552B1 (de) | 1999-12-01 |
Family
ID=6485117
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP94103494A Expired - Lifetime EP0627552B1 (de) | 1993-04-08 | 1994-03-08 | Kraftstoffeinspritzpumpe |
Country Status (4)
Country | Link |
---|---|
US (1) | US5413080A (de) |
EP (1) | EP0627552B1 (de) |
JP (1) | JPH074272A (de) |
DE (2) | DE4311672A1 (de) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0814067A (ja) * | 1994-06-24 | 1996-01-16 | Zexel Corp | 燃料噴射ポンプのサーボバルブ式タイマ |
GB9826348D0 (en) * | 1998-12-02 | 1999-01-27 | Lucas Ind Plc | Advance arrangement |
DE19812698A1 (de) * | 1998-03-23 | 1999-09-30 | Volkswagen Ag | Einrichtung zum Regeln des Spritzbeginns in einer Verteiler-Kraftstoffeinspritzpumpe für Verbrennungsmotoren |
DE19935211A1 (de) * | 1999-07-27 | 2001-02-01 | Deutz Ag | Hydraulischer Förderbeginn-Versteller |
US20070056287A1 (en) * | 2005-09-13 | 2007-03-15 | Cyclone Technologies Lllp | Splitter valve in a heat regenerative engine |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5339528B1 (de) * | 1971-03-06 | 1978-10-21 | ||
US4132508A (en) * | 1974-10-01 | 1979-01-02 | C.A.V. Limited | Fuel injection pumping apparatus |
DE2648043C2 (de) * | 1976-10-23 | 1984-05-24 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstoffeinspritzpumpe für Brennkraftmaschinen |
DE2923445A1 (de) * | 1979-06-09 | 1980-12-18 | Bosch Gmbh Robert | Steuereinrichtung fuer eine kraftstoffeinspritzpumpe |
DE3121635A1 (de) * | 1981-05-30 | 1982-12-23 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
DE3203583A1 (de) * | 1982-02-03 | 1983-08-11 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen mit spritzzeitpunktverstellung |
DE3822257A1 (de) * | 1988-07-01 | 1990-01-04 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
DE3827206A1 (de) * | 1988-08-11 | 1990-02-15 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
US5180290A (en) * | 1989-06-02 | 1993-01-19 | Lucas Industries | Fuel injection pumping apparatus |
DE3943246A1 (de) * | 1989-12-29 | 1991-07-04 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe |
GB9026013D0 (en) * | 1990-11-29 | 1991-01-16 | Lucas Ind Plc | Fuel pumping apparatus |
DE4117813A1 (de) * | 1991-05-31 | 1992-12-03 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
US5462033A (en) * | 1992-04-09 | 1995-10-31 | Lucas Industries Public Limited Company | Fuel pumping apparatus |
-
1993
- 1993-04-08 DE DE4311672A patent/DE4311672A1/de not_active Withdrawn
-
1994
- 1994-03-08 DE DE59408957T patent/DE59408957D1/de not_active Expired - Fee Related
- 1994-03-08 EP EP94103494A patent/EP0627552B1/de not_active Expired - Lifetime
- 1994-04-07 JP JP6069738A patent/JPH074272A/ja active Pending
- 1994-04-08 US US08/225,113 patent/US5413080A/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
DE59408957D1 (de) | 2000-01-05 |
US5413080A (en) | 1995-05-09 |
JPH074272A (ja) | 1995-01-10 |
DE4311672A1 (de) | 1994-10-13 |
EP0627552A1 (de) | 1994-12-07 |
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