EP0282508B1 - Brennstoffeinspritzvorrichtung für eine dieselbrennkraftmaschine mit voreinspritzung - Google Patents

Brennstoffeinspritzvorrichtung für eine dieselbrennkraftmaschine mit voreinspritzung Download PDF

Info

Publication number
EP0282508B1
EP0282508B1 EP87905421A EP87905421A EP0282508B1 EP 0282508 B1 EP0282508 B1 EP 0282508B1 EP 87905421 A EP87905421 A EP 87905421A EP 87905421 A EP87905421 A EP 87905421A EP 0282508 B1 EP0282508 B1 EP 0282508B1
Authority
EP
European Patent Office
Prior art keywords
piston
line
valve
fuel
pump
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
EP87905421A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0282508A1 (de
Inventor
Peter Fuchs
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.)
MAN B&W Diesel AS
Original Assignee
Nova Werke 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 Nova Werke AG filed Critical Nova Werke AG
Priority to AT87905421T priority Critical patent/ATE61449T1/de
Publication of EP0282508A1 publication Critical patent/EP0282508A1/de
Application granted granted Critical
Publication of EP0282508B1 publication Critical patent/EP0282508B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06—Pumps peculiar thereto
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention relates to a fuel injection device for a diesel internal combustion engine in which an injection nozzle is connected to a fuel pump via a pressure line, the fuel pump has a cylinder with at least one fuel line for the inflow and outflow of fuel and a pump chamber and a pump piston, the pump piston at least an annulus connected to the pump chamber with two control edges and the cylinder has an associated relief bore for interrupting the pressure build-up in the pump chamber, the pump piston is connected to a drive unit that is independent of the fuel system and is operated with a pressure medium, and this drive unit is an axial piston unit, a pressure source and a control device having.
  • Fuel injection devices of this type are used in internal combustion engines in which the main injection phase is preceded by a pre-injection. As is known, this can reduce the load on the engine components and improve the combustion process in the internal combustion engine.
  • Such an injection device is known from US Pat. No. 4,426,198, this device having a piston with an oblique control edge and being driven by a camshaft.
  • the pump housing is provided in a known manner with a fuel chamber, into which inlet bores for the fuel open, and from which a pressure line to the injection nozzle going out.
  • the end face of the pump piston and the edges of an annular space on the piston skirt form control edges and interact in a known manner with the inlet bores.
  • a second annular space is arranged below the first annular space with the bevel edge, which is connected to the fuel chamber.
  • This annulus is also in communication with the fuel chamber of the pump, ie the pump chamber.
  • a relief bore is arranged in the pump housing and is connected to the drain line for the fuel.
  • the inflow lines for the fuel and the relief bore are closed by the piston and pressure is built up in the pump chamber. This pressure is released again as soon as the lower annulus clears the relief bore, which also interrupts the injection process.
  • the duration of the interruption depends on the dimensions of the second annular space and the speed of the upward movement of the piston. The interruption occurs at a time when the piston already has a relatively high speed.
  • the cam disc accelerates and moves the piston, and the movement path of the piston is lost. So that the fuel displaced in the pump chamber can flow off, the annular space and the relief bore must have relatively large dimensions, which leads to increased leakage.
  • a fuel pump is known in which the pump piston is driven by a drive piston which is pressurized with pressure medium.
  • the use of a liquid or a gas is proposed as a pressure medium for driving the drive piston.
  • the movements of the drive piston are controlled in a known manner via a multi-way valve in the pressure medium supply line.
  • a pressure medium reservoir is located upstream of the reusable valve.
  • An electrical control device processes measurement signals from the combustion chamber and from the crankshaft of the engine and generates control signals for the control valve in the pressure medium supply line.
  • the stroke of the pump piston is determined by the stroke of the drive piston, ie by means of the electrical control device.
  • the pump piston Since this control is very imprecise, the pump piston has two oblique control edges, and an inlet bore and an outlet bore for the fuel are arranged in the pump cylinder. These two holes are opened and / or closed by the two control edges on the pump piston.
  • This control has the known shortcomings, and only the beginning and the end of the injection process are controlled. An interruption of the lifting process to generate a pre-injection is not possible in the practical version, since the control processes via the drive piston are far too imprecise and too slow.
  • the entire system of the drive piston and the pressure medium also acts as a spring, which leads to undesirable decelerations or accelerations of the pump piston.
  • Such shocks and vibrations disrupt the control processes and lead to defects in the Controls and lines.
  • the delays between the measurements on the engine and the movement corrections on the drive piston in the pump are much too great, which makes the injection processes inaccurate. This leads to a loss of performance and increased pollution.
  • the invention has for its object to provide a fuel injection device, which allows the use of a pressure medium-actuated drive even in injection processes with pre-injection, in which the piston speed is reduced during the interruption phase and the entire stroke of the pump piston is increased and the injection pressure can be increased at the same time.
  • the drive should be switched so quickly that the movements of the pump piston can be controlled.
  • the device is intended to enable the precise interruption of the injection phase even in the case of high-speed engines and to allow the pre-injection, the interruption and the main injection phase to be changed depending on the operating state.
  • the device should also have a mechanical emergency running device.
  • a first control device comprises a main slide and an auxiliary slide for the pressure medium, the main and auxiliary slide each have a reset piston, these reset pistons are connected via a line to the pump chamber and are acted upon by fuel in which Fuel line on the pump is a second control device with an overflow / suction valve and at least one interrupter valve, and the overflow / suction valve has a switching piston unit, the piston chamber via a first line with the relief bore on the pump cylinder and the pump chamber and via a second line the interrupter valve and then the fuel line is connected.
  • the drive unit acted upon by a pressure medium has a first control device with a main and auxiliary slide which regulates the inflow and outflow of pressure medium to the axial piston unit.
  • This pressure medium system is separate from the fuel system and allows the use of particularly suitable pressure media, e.g. High pressure hydraulic oil too.
  • the fuel system of the fuel pump and the pressure medium system of the axial piston unit are mutually independent systems which are linked to one another only via the return pistons of the first control device.
  • the main and auxiliary slides of the first control device have reset pistons which are connected to the pump chamber and acted upon by fuel. This connecting line from the pump chamber to the reset piston of the control device enables the pressure system to be directly influenced by the fuel system.
  • the first control device is acted upon by fuel under high pressure at a desired point in time and the pressure medium system of the axial piston unit is controlled.
  • the second control device arranged in the fuel system allows the control of the inflow and outflow of fuel and at the same time the influencing of the first control device as a function of the pressure in the pump chamber.
  • This arrangement has the advantage that the phases of the injection process are controlled directly with the aid of the fuel pressure and the piston movement.
  • the relief bores in the pump cylinder only serve to transmit pressure surges and the device therefore allows very high piston speeds and the use of all types of fuel.
  • the length of the interruption phase can be changed during the injection phase by means of the interruption valve on the second control device.
  • a preferred embodiment of the invention is characterized in that the cylinder of the pump in the upper In the area of at least one fuel feed line to the pump chamber and in the range of movement of the piston has a first relief bore and a second relief bore arranged below the first, these relief bores are parts of the lines between the pump chamber and the return piston and the switching piston unit and on the jacket of the pump piston three annular spaces with two each Control edges are arranged and connected to the pump chamber via a channel.
  • a connecting line with a check valve is arranged between the piston chamber of the reset piston on the auxiliary slide and the piston chamber of the reset piston on the main slide, and the piston chamber of the reset piston on the auxiliary slide is connected via a further line to the piston chamber of the switching piston of the second control device.
  • the arrangement of three annular spaces with control edges on the pump piston and two relief bores on the pump cylinder enables the main and auxiliary spool on the first control device and the switching points in the second control device to be controlled correctly. Additional interruptions in the injection phase can be achieved by arranging further annular spaces with control edges.
  • the relief bore and the annular spaces serve only to transmit pressure surges and, because the flow rates are very small, can have small dimensions.
  • the main slide has three annular spaces separated by locking seats and two interconnected slide bodies and the auxiliary slide has two annular spaces separated by a locking seat and a slide body, with a connecting line between the central annular space of the main slide and one of the annular spaces of the auxiliary slide is arranged, a pressure line and a return line to each of the other annular spaces of the main slide, and the second annular space of the auxiliary slide is connected via a line to the axial piston unit.
  • a Further improvement of the fuel injection device can be achieved in that in a first switching position of the main slide a slide body blocks the pressure line and the return line is connected to the connecting line to one of the annular spaces of the auxiliary slide, and in a second switching position the other slide body blocks the return line and the pressure line is connected to the connecting line to the auxiliary slide.
  • the slide body of the auxiliary slide expediently has a throttle bore, and this throttle bore connects the two annular spaces to one another when the locking seat is closed.
  • a preferred embodiment of the invention is characterized in that in a first switching position of the auxiliary slide the slide body releases the locking seat and the line to the axial piston unit is connected directly to the connecting line to the main slide, and in a second switching position the slide body blocks the line to the axial piston unit and over the throttle bore between the two annular spaces forms a restricted flow channel.
  • the full volume flows to the axial piston unit and moves the piston at normal speed.
  • the auxiliary slide takes the second switch position when the first annular space on the pump piston interacts with the first relief bore on the pump cylinder.
  • the fuel under pressure moves the auxiliary slide over the return piston.
  • the throttle bore arranged in the slide body of the auxiliary slide only allows a reduced volume flow from the pressure medium source to the axial piston unit.
  • the speed of movement of the pump piston is thereby reduced, the reduction being controllable by changing the throttle cross section. From this follows the advantage that practical during the interruption phase of the injection no stroke volume or working distance of the pump piston is lost.
  • the second control unit has two interrupter valves, both valves are each provided with a control piston, a connecting line is present between the valve chamber of one of the interrupter valves and the piston chamber of this interrupter valve, and an auxiliary valve is arranged in this connecting line. Furthermore, the piston chamber of the second interrupter valve is connected via a line to the lower relief bore on the pump cylinder, and a spring opens the valve in the depressurized state.
  • the second interrupter valve is preferably provided with a spindle which is led out of the control unit.
  • the piston of the auxiliary valve is loaded with a spring and in the depressurized state the valve is open, the piston chamber of the valve being connected via a line to the connecting line between the main and auxiliary slide and in this line a switching valve with a connection to the return line is installed.
  • the two interrupter valves or their piston chambers are connected to the fuel system and the pump chamber via lines and are controlled by pressure surges. These two valves are switched so that one is normally open and the other is closed. This arrangement allows very fast switching operations, since during the opening movement of one interrupter valve the other can already be closed and vice versa. In addition, the second control unit and the pump remain functional even if the control elements fail.
  • the interrupter valves can also be controlled indirectly mechanically or electrically.
  • the direct hydraulic control has the advantage that no additional switching media are necessary and the external influences on the control are thereby reduced.
  • the switching valve which controls the auxiliary valve is a hydraulic valve which is actuated electrically in a known manner. The electrical signals are generated in a known manner by the crank mechanism, the pulse generator or other power-dependent measuring points. A cam control is also suitable for controlling the hydraulic valve.
  • a check valve is arranged in the bore connected to the fuel discharge line in the second control device, and this check valve closes off the bore leading to the interrupter valve and has a free passage in the direction of the bore connected to the fuel line.
  • the slide body of the main slide is connected to a push rod, at least part of the push rod forms the core of a solenoid coil, and this solenoid coil is connected to an electrical pulse generator and / or the push rod is part of a mechanical locking device and attaches this locking device the push rod and the slide body of the main slide in a control position.
  • a preferred embodiment of the invention is characterized in that a camshaft control is connected to the first control device in the hydraulic system, and a cam disk of this camshaft control acts on the push rod of the control device.
  • a camshaft control is connected to the first control device in the hydraulic system, and a cam disk of this camshaft control acts on the push rod of the control device.
  • the piston of the axial piston unit is double-acting and has a full and a reduced piston area
  • the pressure medium supply line to the working space of the axial piston unit, which is assigned to the fully loaded piston surface is via the control device to the pressure source and a pressure medium supply line from an annular space
  • Axial piston unit, which is assigned to the reduced annular area of the piston, is led directly to the pressure source.
  • the pump piston When the fuel injection device according to the invention is operated, the pump piston is rotated about its longitudinal axis depending on the engine output by means of a control device known per se and brought into a position in which the control edges effect the injection of the desired amount of fuel.
  • the start of the injection process is effected via the first control device in the pressure medium system by means of an electrical pulse via the magnetic coil or by means of the control camshaft.
  • the first control device releases the pressure medium flow to the axial piston unit and this moves the pump piston, the fuel in the pump chamber being pressurized.
  • the control valve to the injection nozzle opens and the fuel is injected into the diesel engine under pressure up to 2000 bar.
  • the pump space is coupled to the two control devices via the first relief bore and the connecting lines, and the sudden pressure surge which propagates at the speed of sound causes the return pistons resetting of the auxiliary slide in the first control device and thereby blocking the main flow of pressure medium to the fully loaded piston surface of the axial piston unit.
  • the feed of the axial and the pump piston takes place only by means of the reduced pressure medium flow through the throttle bore of the auxiliary slide.
  • the pressure surge acts on the switching piston unit of the second control device and opens the overflow / suction valve.
  • the pressure prevailing in the pump chamber is released via the feed line into the fuel discharge line and the injection process is interrupted.
  • the pre-injection phase can be adjusted in a known manner by rotating the piston about the longitudinal axis.
  • the pump piston is ready to continue the injection and moves at a reduced speed.
  • the closed interrupter valve is opened, thereby relieving the pressure on the piston chamber of the switching piston unit. The consequence of this is that the reset piston on the auxiliary slide of the first control unit is also relieved and the spring-loaded slide is pushed back into its first switching position.
  • the full volume flow of pressure medium hits the axial piston again, and the movement of the pump piston continues at full speed.
  • the overflow / suction valve closes immediately and pressure is built up again in the pump room.
  • the control valve opens the supply line to the injection nozzle and the main injection phase begins. During this phase, the interrupter valve in the second control device is closed again.
  • the overflow / suction valve is opened again in the manner described and the main injection phase is interrupted.
  • the third annular space on the pump piston is arranged parallel to the second, and the upper control edges of the two annular spaces are at the same distance from one another as the first and the second relief opening. Weber therefore connects the connecting lines with the pressure surge simultaneously on the two return pistons of the auxiliary and main spool on the first control device and on the switching piston unit of the second control device.
  • the main slide opens the return in Pressure medium system, which means that when the overflow / suction valve in the fuel system is opened, the axial piston also stops and returns immediately. This ensures the immediate closure of the injection line and prevents pumping.
  • the pump piston and the axial piston are pushed into their initial positions at bottom dead center.
  • the control edge lies on the upper end face of the piston under the first relief bore. This means that the entire fuel system, including the return pistons, is under the same pressure.
  • the auxiliary slide also moves to its starting position and the control devices are ready for the next work cycle.
  • the stroke of the pump piston is not limited by mechanical elements.
  • the piston can therefore have a smaller diameter and a larger stroke than the known devices. This creates more space for the control edges, which simplifies manufacture and adjustment.
  • this fuel injection device is extremely precise.
  • the start of the injection process can be precisely determined by known and proven means and transmitted to the first control device.
  • the connection of the bevel edge control on the pump piston with a drive unit pressurized with pressure medium results in a very high level of operational reliability and design independence.
  • a great advantage of this fuel injection device is also that all components can be arranged axially to one another, and if several injection devices are arranged, each is independent of the other.
  • the heavy and complex drive camshafts are eliminated complete, which is particularly important for large and fast-running diesel engines. Nevertheless, the emergency control via camshaft controls with a light camshaft is guaranteed.
  • the fuel injection device shown in FIG. 1 has a fuel pump 3, an axial piston unit 28, a first control device 38, a second control device 50 and an injection nozzle 1.
  • the fuel pump 3 comprises a pump cylinder 4, a pump chamber 6, a pump piston 7 and a fuel line, which consists of the fuel feed line 14, the check valve 16, the fuel channel 5, the flow line 66, the feed line 13 and the fuel discharge line 15.
  • a pressure line 2 is arranged, which contains a control valve 17 and leads to the injection nozzle 1.
  • the feed line 13 is inserted into the pump chamber 6 at the upper end thereof.
  • the pump piston 7 has a plurality of annular spaces 18, 19, 20 on its jacket, which are connected to the pump space 6 via a channel 10.
  • the first annular space 18 has control edges 22, 23, the second annular space 19 has control edges 24, 25 and the third annular space 20 the control edge 26.
  • the upper end surface 9 of the pump piston 7 forms a first control edge 21.
  • a first relief bore 11 and a second relief bore 12 are arranged in the pump cylinder 4. When the pump piston 7 is at bottom dead center, the first relief bore 11 opens into the pump chamber 6 above the upper end face 9 of the pump piston 7.
  • the second relief bore 12 is arranged at a distance from the first relief bore 11 which corresponds to the maximum stroke of the pump piston 7 .
  • the pump piston 7 can also be rotated about its longitudinal axis 8, for which purpose a known adjusting device 125 is provided. Furthermore, the pump piston 7 is connected at its lower end to the axial piston unit 28 of a drive unit 27.
  • the axial piston unit 28 consists of a cylinder 29 and a double-acting axial piston 30 and is connected via pressure medium lines 35, 36 to a pressure source 37 which also belongs to the drive unit 27.
  • the double-acting axial piston 30 has a piston surface 31 directed against the working space 33, which is opposite an annular surface 32 assigned to the annular space 34.
  • the drive unit 27 is operated with any known pressure medium and forms a pressure medium system. High-pressure hydraulic oil is used in the present example.
  • the first control device 38 which has a pressure line 42, a return line 43 and a leak line 44, is also located in the pressure medium system.
  • the pressure medium line 35 which opens into the working space 33 of the axial piston unit 28, is also connected to the first control device 38.
  • connecting lines 45, 46 which lead to the relief bores 11 and 12 on the pump cylinder 4, are connected to the first control device 38.
  • the connecting lines 45, 46 are connected to one another via a further connecting line 47, in which a check valve 48 is installed.
  • This check valve 48 prevents fuel from the line 46 flows to line 45 or to the main slide.
  • An electrical pulse generator 39 is arranged next to the first control device 38 and connected to it. This pulse generator 39 is connected in a known manner to the other measuring and control elements of the internal combustion engine and controls the injection processes according to the needs.
  • a pressure control valve 40 and a pressure medium and expansion tank 41 are arranged in the drive unit 27 or in the pressure medium system in a known manner.
  • the connecting line 46, the flow line 66 and the feed line 13 are connected to the second control device 50.
  • This has a through bore 64, which is connected on the one hand to the throughflow line 66 and on the other hand to the fuel line 15.
  • An overflow / suction valve 51 is installed in this bore and has a valve seat 61, a valve stem 58 and a switching piston 52.
  • a fuel pump (not shown) is arranged in the fuel feed line 14, which pumps the fuel under low pressure in the fuel system.
  • the overflow / suction valve 51 is loaded with a spring 59 which closes the valve seat 61.
  • the switching piston 52 which rests on the valve stem 58.
  • a piston chamber 57 is formed below the switching piston 52 and is connected to the connecting line 46 and the relief bore 11 via a line 49.
  • a spring 60 is arranged in the piston chamber 57, which presses the switching piston 52 against the valve stem 58 and relieves the overflow / suction valve 51 against the contact pressure of the spring 59 and keeps it balanced.
  • Liver the bores 63, 65 and an interrupter valve 53 is the piston chamber 57 also in connection with the bore 64 or the fuel discharge line 15.
  • a compensating valve 54 is connected, which facilitates the afterflow of fuel into the various bores.
  • a check valve 55 arranged opposite the interrupter valve 53 prevents pressure surges in the bore 64 from opening the closed interrupter valve 53. Such pressure surges can occur when the overflow / suction valve 51 is opened at high pressure in the pump chamber 6 and the pump pressure flows through the feed line 13 into the bore 64 and the fuel line 15. Depending on the pressure in the pump chamber 6, such pressure surges can briefly reach up to 200 bar.
  • the interruption valve 53 is actuated by a control 56, which is a known electrical control or a mechanical control, which is connected to the camshaft control acting on the first control device 38.
  • the first control device 38 is shown in section in FIG. 2 and essentially consists of a main slide 70, an auxiliary slide 71, a mechanical locking device 69 and a camshaft control 110.
  • the main slide 70 has two slide bodies 77, 78 with control edges and locking seats 82, 83 on.
  • An annular space 79 is assigned to the slider body 77 and an annular space 81 is assigned to the slider body 78.
  • Pressure relief spaces and sealing pistons are arranged behind each of the slide bodies 77 and 78, the pressure relief spaces being connected to a leakage line 44.
  • the slide bodies 77, 78 and the sealing pistons are arranged at the correct distance from one another by means of a core and are connected to one another.
  • the annular space 81 is connected to the return line 43, the annular space 79 to the pressure line 42 and 36, and the annular space 80 via a connecting line 89 to an annular space 86 of the auxiliary slide 71.
  • a push rod 96 is arranged, which with the slider bodies 77, 78 is connected, part of the push rod 96 forming the core 98 of a solenoid 97.
  • the push rod 96 extends beyond the magnetic coil 97 and is enclosed by the mechanical locking device 69.
  • the camshaft control 110 is connected to this mechanical locking device 69.
  • a return piston 72 interacts with the slide bodies 77, 78 via a pin 76.
  • a piston chamber 73 belonging to the return piston 72 is connected to the fuel system via the connecting line 45. As shown in FIG. 1, this connecting line 45 is inserted into the relief bore 12 in the pump cylinder 4, which leads into the pump chamber 6. Via the connecting line 47 and the check valve 48, the piston chamber 73 is also connected to the connecting line 46 and thus to the relief bore 11 in the pump cylinder 4 and the piston chamber 57 in the second control device 50.
  • the auxiliary slide 71 has a slide body 84 and two annular spaces 85, 86. Pressure relief spaces and sealing pistons are likewise arranged behind the slide body 84 and the annular spaces 85, 86, the pressure relief spaces being connected to the leak line 44.
  • the locking seat 87 is located between the two annular spaces 85, 86.
  • the annular space 86 is connected to the pressure line 42 or the return line 43 via the connecting line 89.
  • the pressure medium line 35 extends from the annular space 85 and leads to the working space 33 of the axial piston unit 28.
  • auxiliary slide 71 In the slide body 84 there is a throttle bore 88, which enables a reduced flow of hydraulic oil from the annular space 86 into the annular space 85 and vice versa even when the locking seat 87 is closed.
  • the auxiliary slide 71 also interacts with a return piston 74 at one end.
  • a piston chamber 75 belonging to the return piston 74 projects beyond the Connection line 46 with the fuel system or with the relief bore 11 on the pump cylinder 4 and the piston chamber 57 in connection with the second control device 50.
  • the auxiliary slide 71 On the opposite side, the auxiliary slide 71 is loaded with a spring 94 arranged in the leakage space 95, which pushes the auxiliary slide 71 back into the starting position.
  • FIG. 2 shows the mechanical locking device 69 and the camshaft control 110.
  • the mechanical locking device 69 consists essentially of a locking body 100, pawls 104 and unlocking bolt 106.
  • the push rod 96 projects into the locking body 100 and has a shoulder 101 in the area thereof. If the push rod 96 is moved to the left by means of the solenoid coil 97, the shoulder 101 takes the locking body 100 with it, and the spring-loaded pawls 104 snap into the cams 105 and helped the locking body 100 in its position. As a result, the current supply to the solenoid coil 97 can be interrupted and there is no risk of overloading or overheating.
  • the push rod 96 is reset at the end of the injection process via the return piston 72, which is acted upon by the injection pressure.
  • the push rod 96 is pressed to the right against the force of the spring 102 and the unlocking bolts 106 are driven outwards from the end of the push rod 96.
  • These unlocking bolts 106 raise the pawls 104 and thereby release the cams 105 on the locking body 100.
  • the spring 103 now pushes the locking body 100 back into its starting position.
  • the camshaft control 110 is arranged in addition to the solenoid 97 of the injection control. This consists of the cam disk 107 with a cam 108 and the idler roller 109 attached to the control body 100.
  • the camshaft is driven by a drive, not shown, which communicates with the crank mechanism.
  • the cam 108 drives the blocking body 100 and thus the push rod 96 to the left at the start of the injection process via the idler roller 109.
  • the movement of the control body 100 and the push rod 96 requires only slight forces, and the camshaft control 110 can therefore be built easily and without great kinematic effort.
  • the push rod 96 is reset at the end of the injection process in the same way as described above.
  • a second magnetic coil 99 is arranged in addition to the magnetic coil 97.
  • Both solenoids 97, 99 receive electrical pulses from the electrical pulse generator 39 via the electrical line 93.
  • the solenoid 99 By actuating the solenoid 99 with an electrical pulse, the push rod 96 can be shifted to the right and the injection process can therefore be stopped prematurely. This enables an emergency stop of the injection device, since this action of the main slide 70 interrupts the action on the axial piston 30 of the axial piston unit 28 and pushes the axial piston 30 back.
  • the second control device 50 shown in FIG. 3 is an embodiment which allows higher switching speeds and fulfills emergency operation functions.
  • This improved control device has, in the same way as that shown in FIG. 1, an overflow / suction valve 51 with a switching piston 52, a compensation valve 54 and a check valve 55.
  • Fuel flows from the throughflow line 66 into the overflow chamber 62 and from there either over the overflow - / Suction valve 51 and the feed line 13 into the pump chamber 6 or via the bore 64 to the fuel discharge line 15.
  • the check valve 55 has a free passage 68 through which the fuel can flow from the bore 64 into the line 15. When the check valve 55 is open, the Valve chamber 114 in connection with the fuel discharge line 15 via the bore 67. As can be seen in FIG.
  • the piston chamber 57 of the switching piston 52 is connected to the relief bores 11 and 12 in the pump cylinder 4 via the line 49 and the lines 45 and 46.
  • a second interrupter valve 111 is installed in the bores 63, 65 between the piston chamber 57 and the fuel discharge line 15.
  • a further auxiliary valve 117 is arranged next to the interrupter valve 53.
  • the interrupter valve 111 has a control piston 113 and a piston chamber 118, the piston chamber 118 being connected via the line 119 to the line 45 or the relief bore 12. If there is no pressure in the piston chamber 118, the interrupter valve 111 is pressed against the lower stop by a spring 120 and is open.
  • the interrupter valve 53 has a control piston 112 and a piston chamber 115 which is connected to the valve chamber 114 via the line 116.
  • the interrupter valve 53 is pressed against the valve seat by a spring 126 when there is no pressure in the piston chamber 115 and keeps this valve closed.
  • the auxiliary valve 117 which has a piston 121, a piston chamber 123 and a spring 122, is arranged in the line 116 between the piston chamber 115 and the valve chamber 114. In the depressurized state, the spring 122 presses the piston 121 against the stop, and the auxiliary valve 117 is open.
  • the piston chamber 123 is connected via the line 124 to a switching valve 90, which is connected to the auxiliary slide 71 of the control device 38 via the control lines 91, 92.
  • the control line 91 opens into the annular space 86 and the control line 92 into the leak space 95 connected to the leak line on the auxiliary slide 71.
  • the switching valve 90 is a three-way valve which is actuated electrically by the pulse generator 39 or by a camshaft .
  • the fuel injection device shown in FIG. 1 is operated in such a way that fuel flows from the fuel feed line 14 via the fuel channel 5, the line 66, the open suction valve 51 and the feed line 13 into the pump chamber 6.
  • the pump piston 7 is in its lowest position and the axial piston 30 connected to the pump piston 7 is also at the bottom dead center.
  • the main slide 70 of the first control unit 38 is held in its initial position by the spring 103, and the slide body 77 closes the connection of the pressure line 42 to the pressure medium line 35.
  • the magnetic coil 97 is excited by the electrical pulse generator 39 and via the push rod 96 the main slide 70 is displaced in the direction of the return piston 72.
  • the slide body 77 releases the connection between the annular space 79 and the annular space 80.
  • the slide body 78 closes the connection between the annular space 80 and the annular space 81.
  • Pressure medium thus flows under pressure from the pressure line 42 via the line 89 into the annular spaces 86, 85 on the auxiliary slide 71 and into the line 35 and thus into the working space 33 Axial piston unit 28.
  • the axial piston 30 moves upward and pushes the pump piston 7 in the direction of the upper end of the pump chamber 6. This axial movement closes the relief bore 11 in the pump cylinder 4 and pressure is built up in the pump chamber 6.
  • the control valve 17 opens and fuel is injected into the combustion chamber of a diesel internal combustion engine via the injection nozzle 1.
  • the pressure prevailing in the pump chamber 6 is supplied to the annular spaces 18, 19 and 20 via a channel 10 attached to the jacket of the pump piston 7.
  • the switching piston 52 is acted upon by the pressure surge in the second control device 50 via the piston chamber 57.
  • the switching piston 52 moves upward and opens the overflow / suction valve 51 or its valve seat 61 via the valve stem 58.
  • the pressure prevailing in the pump chamber 6 thus immediately relaxes in the overflow chamber 62, the bore 64 and in the fuel discharge line 15.
  • the sudden Pressure drop causes the control valve 17 to close immediately and the injection process is interrupted.
  • the relief bore 11 is closed again after a short movement of the piston 7 by the lower control edge 23 of the annular space 18, and the overflow / suction valve 51 is held in the open position by the fuel volume in the piston space 57.
  • the pressure in space 57 is higher than in space 62.
  • the springs 59, 60 support the movements of the valve 51. Since the annular space 18 only has to serve to transmit the pressure surge, the distance between the control edges 22, 23 can be chosen to be very small .
  • the interruption valve 53 is opened quickly by the control 56 being actuated.
  • the bore 65 is connected to the fuel discharge line 15 and the auxiliary slide 71 in the first control device 38 can be pushed back into its starting position by the spring 94.
  • the overflow / suction valve 51 is closed by the same pressure relief. As a result, the full volume flow again flows into the pressure line 35 and the movement of the axial piston 30 and thus of the pump piston 7 becomes full Speed continued.
  • the control valve 17 opens again and the main phase of the injection begins. During this phase, the interrupter valve 53 is closed again with the aid of the control 56.
  • the main injection phase continues until the control edges 24 and 26 of the two annular spaces 19 and 20 reach the relief bores 11 and 12.
  • the two control edges 24 and 26 are arranged at the same distance from one another as the two relief bores 11 and 12.
  • the pressure prevailing in the pump chamber 6 is transmitted to the two control devices 38 and in the form of a pressure surge via lines 45, 46 and 49 50 transferred.
  • the return piston 72 is acted upon by the pressure surge in the line 45 and via the piston chamber 73 and the main slide 70 is pushed back.
  • the slide body 77 interrupts the connection between the annular spaces 79 and 80, and the slide body 78 opens the connection between the annular spaces 80 and 81, with which the working space 33 on the axial piston unit 28 is connected to the return line 43. Since the auxiliary slide 71 has also been displaced by the pressure surge on the return piston 74, the locking seat 87 is closed by the slide body 84. The pressure medium can therefore only flow back from the working space 33 via the line 35 and the throttle bore 88 at a limited speed, thereby preventing the piston from shooting back. At the same time, as already described above, the overflow / suction valve 51 on the second control device 50 opens the valve seat 61, and the pressure in the pump chamber 6 is immediately reduced.
  • the control valve 17 closes and the main injection process is ended.
  • the entire fuel system and thus also the annular spaces 18, 19 and 20 on the pump piston 7 and the lines 45, 46, 49 are thus again under the normal pressure of the fuel feed pump and the auxiliary slide 71 is pushed back into the starting position by means of the spring 94.
  • the slide body 84 opens the Lock seat 87 and releases the full cross-section.
  • the pressure of the pressure medium system prevailing in the annular space 34 of the axial piston unit 28 pushes the axial piston 30 back until it has reached its starting position again at bottom dead center. The device is thus ready for a further injection process.
  • interrupter valves 53 and 111 are used in accordance with FIG. 3 in the second control device 50, these valves are also switched with the aid of the pressure surges branched off from the pump chamber 6 via the relief bores 11 and 12.
  • the use of two interrupter valves 53, 111 with corresponding control pistons 112, 113 ensures operation up to the maximum stroke even if the control 56 according to FIG. 1 or the switching valve 90 or its control fails.
  • the auxiliary valve 117 is open in the unpressurized state in the piston chamber 123 by the spring force 122. If the control edge 22 on the piston 7 reaches the relief bore 11, the pressure from the pump chamber 6 acts as a pressure surge from the relief bore 11 via the line 49 and the connecting line 116 to the control piston 112, and the interruption valve 53 opens.
  • the overflow / suction valve 51 closes immediately and the injection is continued.
  • the valve 53 also closes again.
  • the piston 7 continues to move upward, the injection phase being continued.
  • the pressure from the pump chamber 6 acts as a pressure surge via lines 49 and 119.
  • the pressure surge via line 49 acts on the switching piston 52 and opens the overflow / suction valve 51.
  • the second interruption valve 111 is closed simultaneously by the pressure surge from the pump chamber 6 via the relief bore 12, the connecting line 119 and the action on the control piston 113, so that the overflow / suction valve remains open and the injection is ended.
  • the open break valve 111 is kept open by closing the auxiliary valve 117.
  • the switching valve 90 ensures that the auxiliary valve 117 is opened at the right time and thus the interrupter valve 53 is closed.
  • the switching valve 90 for the auxiliary valve 117 is controlled in a known manner as a function of power and speed, as is the control of the adjustment device 125 on the pump piston 7.
  • the combination of these two adjustment options enables the pre-injection, interrupter and main injection phases to be changed over a wide range .
  • further annular spaces with control edges can be arranged on the pump piston 7, as a result of which further interruption phases can be switched on in the injection cycle. Due to the long possible stroke of the pump piston 7, such annular spaces can be easily arranged in a known manner.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
EP87905421A 1986-09-09 1987-09-04 Brennstoffeinspritzvorrichtung für eine dieselbrennkraftmaschine mit voreinspritzung Expired - Lifetime EP0282508B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87905421T ATE61449T1 (de) 1986-09-09 1987-09-04 Brennstoffeinspritzvorrichtung fuer eine dieselbrennkraftmaschine mit voreinspritzung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH3617/86 1986-09-09
CH3617/86A CH671073A5 (pl) 1986-09-09 1986-09-09

Publications (2)

Publication Number Publication Date
EP0282508A1 EP0282508A1 (de) 1988-09-21
EP0282508B1 true EP0282508B1 (de) 1991-03-06

Family

ID=4259828

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87905421A Expired - Lifetime EP0282508B1 (de) 1986-09-09 1987-09-04 Brennstoffeinspritzvorrichtung für eine dieselbrennkraftmaschine mit voreinspritzung

Country Status (11)

Country Link
US (1) US4878471A (pl)
EP (1) EP0282508B1 (pl)
JP (1) JPH0681934B2 (pl)
KR (1) KR940011343B1 (pl)
CN (1) CN1010335B (pl)
AT (1) ATE61449T1 (pl)
CH (1) CH671073A5 (pl)
DE (1) DE3768490D1 (pl)
FI (1) FI882145A (pl)
PL (1) PL157237B1 (pl)
WO (1) WO1988002066A1 (pl)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5392749A (en) * 1991-10-11 1995-02-28 Caterpillar Inc. Hydraulically-actuated fuel injector system having separate internal actuating fluid and fuel passages
US5492098A (en) * 1993-03-01 1996-02-20 Caterpillar Inc. Flexible injection rate shaping device for a hydraulically-actuated fuel injection system
JP2885076B2 (ja) * 1994-07-08 1999-04-19 三菱自動車工業株式会社 蓄圧式燃料噴射装置
US5730104A (en) * 1997-02-19 1998-03-24 Caterpillar Inc. Injection rate shaping device for a fill metered hydraulically-actuated fuel injection system
DE19716221B4 (de) * 1997-04-18 2007-06-21 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung mit Vor- und Haupteinspritzung bei Brennkraftmaschinen, insbesondere für schwer zündbare Kraftstoffe
WO2000070216A1 (en) * 1999-05-18 2000-11-23 International Engine Intellectual Property Company, Llc. Double-acting two-stage hydraulic control device
DE10126686A1 (de) * 2001-06-01 2002-12-19 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung mit Druckverstärker
SE523498C2 (sv) * 2001-08-17 2004-04-27 Volvo Teknisk Utveckling Ab Förfarande för att styra bränsleinsprutningen till ett förbränningsrum samt en bränsleinsprutningsanordning för att genomföra förfarandet
JP3993841B2 (ja) * 2003-06-12 2007-10-17 ヤンマー株式会社 低温始動進角機構を備える燃料噴射ポンプ
KR101219877B1 (ko) * 2011-05-13 2013-01-09 현대중공업 주식회사 디젤엔진용 하이브리드 연료분사 장치
DK179219B1 (en) * 2016-05-26 2018-02-12 Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland Fuel or lubrication pump for a large two-stroke compression-ignited internal combustion engine

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB514011A (en) * 1938-04-26 1939-10-27 Gardner & Sons Ltd Improvements relating to fuel injection pumps for compression ignition oil engines
CH352531A (fr) * 1958-04-12 1961-02-28 Etienne Bessiere Pierre Pompe d'injection
CH589557A5 (pl) * 1974-12-24 1977-07-15 Rieter Ag Maschf
GB1592350A (en) * 1976-11-09 1981-07-08 Lucas Industries Ltd Fuel systems for an internal combustion engine
US4275087A (en) * 1979-05-15 1981-06-23 International Flavors & Fragrances Inc. Flavoring with 2,6,6-trimethyl-α-propenyl-1,3-cyclohexadiene-1-methanol substances
FR2482669A2 (fr) * 1979-05-28 1981-11-20 Semt Perfectionnement a une pompe d'injection pour un moteur a combustion interne
DE3001155A1 (de) * 1980-01-15 1981-07-16 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzanlage fuer selbstzuendende brennkraftmaschine
DE3100725A1 (de) * 1980-12-16 1982-07-01 Gebrüder Sulzer AG, 8401 Winterthur "einrichtung zur gesteuerten foerderung des brennstoffs in einer brennkraftmaschine"
US4417557A (en) * 1981-07-31 1983-11-29 The Bendix Corporation Feed and drain line damping in a fuel delivery system
US4499876A (en) * 1981-10-30 1985-02-19 Nippondenso Co., Ltd. Fuel injection control for internal combustion engines
US4425893A (en) * 1981-12-07 1984-01-17 The Garrett Corporation Fuel injection
US4667638A (en) * 1984-04-17 1987-05-26 Nippon Soken, Inc. Fuel injection apparatus for internal combustion engine
JPS61261653A (ja) * 1985-05-16 1986-11-19 Nippon Soken Inc 燃料供給装置

Also Published As

Publication number Publication date
PL157237B1 (en) 1992-05-29
CN1010335B (zh) 1990-11-07
JPH0681934B2 (ja) 1994-10-19
KR880701825A (ko) 1988-11-05
EP0282508A1 (de) 1988-09-21
FI882145A0 (fi) 1988-05-06
DE3768490D1 (de) 1991-04-11
US4878471A (en) 1989-11-07
PL267641A1 (en) 1988-08-04
JPH01500844A (ja) 1989-03-23
KR940011343B1 (ko) 1994-12-05
ATE61449T1 (de) 1991-03-15
WO1988002066A1 (en) 1988-03-24
CH671073A5 (pl) 1989-07-31
CN87106778A (zh) 1988-06-08
FI882145A (fi) 1988-05-06

Similar Documents

Publication Publication Date Title
DE3511820C2 (pl)
DE3836725C1 (pl)
EP0960274B1 (de) Kraftstoffeinspritzvorrichtung für brennkraftmaschinen
EP0455762B1 (de) Elektrohydraulische ventilsteuervorrichtung für brennkraftmaschinen
DE3638369A1 (de) Steuerventil
DE3148671C2 (pl)
DE2945484C2 (pl)
DE19716750C2 (de) Motorbremssystem für einen Verbrennungsmotor
DE19545162B4 (de) Brennstoffeinspritzvorrichtung mit federvorgespanntem Steuerventil
EP0282508B1 (de) Brennstoffeinspritzvorrichtung für eine dieselbrennkraftmaschine mit voreinspritzung
DE69404799T2 (de) Bremsvorrichtung für eine Brennkraftmaschine
EP0767295B1 (de) Hydraulischer Ventilantrieb
EP1446559A1 (de) Vorrichtung zur steuerung mindestens eines gaswechselventils
EP0281580B1 (de) Brennstoffeinspritzvorrichttung für eine dieselbrennkraftmaschine
EP0455763B1 (de) Hydraulische ventilsteuervorrichtung für eine mehrzylinder-brennkraftmaschine
DE19756087A1 (de) Hochdruckpumpe zur Kraftstoffversorgung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen
EP1925812B1 (de) Kraftstoffeinspritzventil für Brennkraftmaschinen
DE2713805A1 (de) Steuereinrichtung fuer diesel-einspritzbrennkraftmaschinen
DE102015215241A1 (de) Hydraulisch betätigtes Schaltventil
DE3524980C2 (de) Kraftstoffeinspritzpumpe für eine Brennkraftmaschine
DE3543151C2 (pl)
EP0032172B1 (de) Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen, insbesondere für Dieselmotoren
EP0032168B1 (de) Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen, insbesondere für Dieselmotoren
EP0090296A1 (de) Einspritzdüse mit einem Nadelkolben
DE3008070C2 (pl)

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): AT BE CH DE FR GB IT LI LU NL SE

17P Request for examination filed

Effective date: 19880902

17Q First examination report despatched

Effective date: 19890803

ITF It: translation for a ep patent filed
GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

REF Corresponds to:

Ref document number: 61449

Country of ref document: AT

Date of ref document: 19910315

Kind code of ref document: T

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

Ref document number: 3768490

Country of ref document: DE

Date of ref document: 19910411

ET Fr: translation filed
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: CH

Ref legal event code: PLI

Owner name: MAN B&W DIESEL A/S

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732

ITPR It: changes in ownership of a european patent

Owner name: CONCESSIONE DI LICENZA;MAN B & W DIESEL A/S

REG Reference to a national code

Ref country code: FR

Ref legal event code: CL

EPTA Lu: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: LU

Payment date: 19940801

Year of fee payment: 8

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

Ref country code: FR

Payment date: 19940819

Year of fee payment: 8

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

Ref country code: SE

Payment date: 19940822

Year of fee payment: 8

Ref country code: AT

Payment date: 19940822

Year of fee payment: 8

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

Ref country code: BE

Payment date: 19940825

Year of fee payment: 8

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

Ref country code: NL

Payment date: 19940930

Year of fee payment: 8

EAL Se: european patent in force in sweden

Ref document number: 87905421.1

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

Ref country code: GB

Payment date: 19950811

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: 19950814

Year of fee payment: 9

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

Ref country code: DE

Payment date: 19950825

Year of fee payment: 9

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

Ref country code: LU

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

Effective date: 19950904

Ref country code: AT

Effective date: 19950904

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

Ref country code: SE

Effective date: 19950905

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

Ref country code: BE

Effective date: 19950930

BERE Be: lapsed

Owner name: NOVA-WERKE A.G.

Effective date: 19950930

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

Ref country code: NL

Effective date: 19960401

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

Ref country code: FR

Effective date: 19960531

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 19960401

EUG Se: european patent has lapsed

Ref document number: 87905421.1

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: GB

Effective date: 19960904

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

Ref country code: LI

Effective date: 19960930

Ref country code: CH

Effective date: 19960930

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

Effective date: 19960904

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: DE

Effective date: 19970603

NLUE Nl: licence registered with regard to european patents

Effective date: 19920214

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: 20050904