EP2954192A1 - Valve - Google Patents
ValveInfo
- Publication number
- EP2954192A1 EP2954192A1 EP13815445.5A EP13815445A EP2954192A1 EP 2954192 A1 EP2954192 A1 EP 2954192A1 EP 13815445 A EP13815445 A EP 13815445A EP 2954192 A1 EP2954192 A1 EP 2954192A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- recess
- pressure pump
- housing
- fuel
- 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.)
- Granted
Links
- 239000012530 fluid Substances 0.000 claims abstract description 21
- 238000007599 discharging Methods 0.000 claims abstract description 6
- 239000000446 fuel Substances 0.000 claims description 120
- 238000007789 sealing Methods 0.000 claims description 29
- 230000001050 lubricating effect Effects 0.000 claims description 17
- 238000002347 injection Methods 0.000 claims description 12
- 239000007924 injection Substances 0.000 claims description 12
- 238000002485 combustion reaction Methods 0.000 claims description 11
- 239000000314 lubricant Substances 0.000 claims description 8
- 239000003502 gasoline Substances 0.000 claims description 5
- 238000006073 displacement reaction Methods 0.000 claims description 2
- 239000002828 fuel tank Substances 0.000 description 9
- 238000005096 rolling process Methods 0.000 description 8
- 238000005461 lubrication Methods 0.000 description 7
- 230000001105 regulatory effect Effects 0.000 description 7
- 239000004033 plastic Substances 0.000 description 4
- 238000013016 damping Methods 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 230000000295 complement effect Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 229910052751 metal Inorganic materials 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 230000010355 oscillation Effects 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 239000011152 fibreglass Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000000284 resting effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
-
- 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
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
- F02M37/0023—Valves in the fuel supply and return system
- F02M37/0029—Pressure regulator in the low pressure fuel system
-
- 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
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/0047—Layout or arrangement of systems for feeding fuel
- F02M37/0052—Details on the fuel return circuit; Arrangement of pressure regulators
-
- 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
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
Definitions
- the present invention relates to a valve according to the preamble of
- a high-pressure pump permanently ensures the maintenance of the pressure in the
- High pressure accumulator of the common rail injection system can be driven, for example, by a camshaft of the internal combustion engine by means of a drive shaft.
- Rotary vane pump used, which are upstream of the high-pressure pump.
- the prefeed pump delivers the fuel from a fuel tank through a fuel line to the high pressure pump.
- piston pumps are used as high-pressure pumps.
- a drive shaft is mounted. Radially to pistons are arranged in a cylinder.
- a roller with a roller rolling surface On the drive shaft with at least one cam is a roller with a roller rolling surface, which is mounted in a roller shoe.
- the roller shoe is connected to the piston, so that the piston is forced to oscillate translational motion.
- a spring applies to the roller shoe a radially directed to the drive shaft force, so that the roller is in constant contact with the drive shaft.
- the roller stands with the roller rolling surface on a shaft rolling surface as the surface of the drive shaft with the at least one cam in contact with the drive shaft.
- the roller is mounted by means of a sliding bearing in the roller shoe.
- the drive shaft with the at least one cam, the roller and the roller shoe are arranged within a lubricant space of the high-pressure pump.
- fuel delivered by the prefeed pump to the high-pressure pump is passed in order, on the one hand, to lubricate the components within the lubricant space and to cool them with the fuel conducted through the lubricant space.
- the fuel delivered by the prefeed pump to the high-pressure pump thus comprises in volume flow on the one hand the fuel passed through the lubricant space for lubricating and cooling the components of the high-pressure pump within the lubricant space and the fuel intended for the high-pressure pump for delivery under high pressure to the high-pressure rail. It should be on a fuel line from the
- Pre-feed pump to the high-pressure pump is a substantially constant pressure. For this reason, in a flow channel of the
- a spill valve Pre-feed pump to the lubricating space or arranged from the lubricating space to a fuel tank, a spill valve.
- the overflow valve is disposed within a recess of a housing of the high-pressure pump. Above a predetermined pressure, z. B. 5.5 bar, opens the spill valve and thereby passes more fuel through the lubrication chamber and this through the
- Lubricant-led fuel is returned to the fuel tank. At a drop in pressure before the spill valve, z. B. below 4.5 bar, closes the spill valve.
- Such overflow valves have a valve cylinder and a closing piston on which is movably mounted on a cylinder between a closed position and an open position. Through an inlet opening, fuel can be introduced into the overflow valve and discharged out of the overflow valve through a drain opening.
- the pressure of the overflow valve On the one hand the pressure of the overflow valve
- Cylinder space opening drainage openings are in the closed position of Locking piston closed. Only when the pressure at the inlet opening is increased by the fuel does the closing piston move into an open position, in which the outlet openings on the cylinder chamber are not closed by the closing piston.
- the cylinder chamber is in a first Zylinderteilraum and a second
- Cylinder part space as a spring chamber divided by the closing piston In the second cylinder space or spring chamber, the spring is arranged and opens into the spring chamber through the valve cylinder, a compensation opening.
- the spring chamber is filled with fuel during normal operation and the compensation opening serves to allow a lifting movement of the closing piston, since during the lifting movement of the closing piston, the volume of the spring chamber is changed.
- the compensation opening with the spring chamber also causes a damping of the lifting movement of the Sch Strukturkobens, as the displaced by the closing piston in the spring chamber fuel can flow only through the compensation opening at a reduction in the volume of the spring chamber and vice versa.
- Return pressure in the fuel return line can lead to an emptying of the spring chamber or an air filling of the lubricating space. This occurs after a restart of the high-pressure pump to the
- DE 10 2009 026 596 A1 shows a high-pressure pump for conveying a fluid, in particular fuel, comprising a drive shaft, at least one piston, at least one cylinder for supporting the piston, wherein the at least one piston is supported indirectly or directly on the at least one cam, so that of the at least one piston one
- Translational movement is executable due to a rotational movement of the drive shaft.
- Inventive valve in particular overflow valve, for arrangement in a recess of a housing of a high-pressure pump, comprising
- Valve housing with a valve cylinder, a movable within the valve cylinder between a closed position and open position
- Closing piston so that in the closed position, the valve is closed and in the open position, the valve is open, an inlet opening for supplying a fluid within a enclosed by the valve cylinder
- Cylinder space at least one drain opening for discharging the fluid introduced into the cylinder chamber, an elastic valve element connected to the closing piston, in particular valve spring, with which a pressure force can be applied to the closing piston, which can be applied opposite to one of the fluid within the cylinder space on the closing piston
- Compressive force is aligned so that the closing piston by means of the force applied by the elastic valve element and the fluid on the closing piston pressure between the closed position of the open position is movable, wherein the valve housing on the outside no fixing device, in particular no thread or no bayonet connection, for axial attachment in the
- Valve housing is on the outside no fixing device, in particular no thread or no external thread formed, for axial attachment to the housing of the high-pressure pump in the recess. This can be a
- High-pressure pump to be flowed through axially by the fluid.
- the axial fixation of the valve within the recess of the housing takes place in the
- Valve element is disposed within the second cylinder part space as a spring chamber and in the second cylinder part space opens a compensation opening, in particular radially, through the valve housing.
- Valve housing formed and / or arranged. Outside of the valve between the inlet opening and the at least one drain opening can thus flow around the outside of the fluid from the valve in an arrangement in the recess of the housing.
- Inventive high-pressure pump for conveying fuel for.
- As diesel or gasoline comprising a housing, a drive shaft with at least one cam, at least one piston for conveying fuel, at least one cylinder for supporting the at least one piston, wherein the at least one piston indirectly on the drive shaft with the at least one cam supported, so that from the at least one piston, a translational movement due to a rotational movement of the drive shaft is executable, a lubricating space, a recess formed in the housing for arranging a spill valve, a disposed within the recess
- Overflow valve having an inlet opening and at least one drain opening, wherein the recess has a first inner end and a second outer end and the second outer end of the recess for passing fuel through the lubricating space and preferably for discharging fuel from the recess serves as a flow channel.
- the fuel can be passed through the second outer end of the recess, so that advantageously flows through a gap between the valve housing and the housing of the high-pressure pump, starting from the at least one drain opening in the direction of the second outer end of the spill valve of the fuel is and therefore also very easy air in this space by means of passing fuel through the gap can be easily removed at the second outer end by the supply of fuel.
- Recess inlet channel and the inlet opening of the overflow valve has a smaller distance in the direction of a longitudinal axis of the recess to a mouth of Aussparungszulaufkanales in the recess as the at least one drain opening of the spill valve and / or the recess is formed as a bore.
- Fuel can be introduced into the recess through the recess inlet channel and from a portion of the recess, starting at the first inner end, to the inlet opening of the recess
- Overflow valve can thus be the fuel from the recess inlet channel through the recess in the inlet opening of the spill valve initiated.
- Overflow valve formed a sealing ring and preferably the sealing ring is aligned in the direction of the longitudinal axis of the recess between the inlet opening and the at least one drain opening.
- the sealing ring divides the
- nozzle in particular a return pipe, with a
- Socket channel disposed within the recess and the nozzle channel is used for passing fuel.
- Overflow valve on the neck so that thereby the spill valve is fixed in the axial direction in the recess.
- the second outer end of the overflow valve, in particular of the valve housing rests on the connecting piece, so that thereby the overflow valve in the axial direction in the recess is attached.
- the overflow valve in the axial direction in addition to the sealing ring on the housing of the high-pressure pump, so characterized thereby the valve in both axial directions on the housing of the
- the neck is by means of a
- the nozzle is particularly simple and reliable on the housing of the high-pressure pump within the recess.
- the overflow valve of the high pressure pump is designed as an overflow valve described in this patent application.
- High pressure pump a, in particular annular, space formed for passing the fuel from the drain opening to the outer axial end of the spill valve and preferably to the second end of the recess.
- the fuel can flow into the first cylinder subspace through the inlet opening of the valve and flow out of it through at least one discharge opening into the intermediate space.
- the fuel emerging from the at least one drain opening flows around the overflow valve between the valve housing and the housing of the high-pressure pump in the axial direction, that is to say in the direction of a longitudinal axis of the valve from the first inner end of the overflow valve to a second outer end of the overflow valve.
- the stroke volume of the valve piston is greater than the volume of the gap.
- Valve piston is the volume in the first and / or second cylinder part space, which of the closing piston between the open position and the
- the gap is in an axial
- Valve housing opens from the second cylinder space or spring chamber to the gap between the valve housing and the housing of the high-pressure pump. With air in the sub-gap can thus by a movement or lifting movement of the closing piston between the
- the inlet opening of the overflow valve is formed at an inner axial end of the overflow valve.
- Inventive high-pressure injection system for an internal combustion engine in particular for a motor vehicle, comprising a high pressure pump with a lubrication chamber and an overflow valve, a prefeed pump, a high-pressure rail, wherein the spill valve is designed as a described in this patent application spill valve and / or the high-pressure pump as one in this Patent application described high-pressure pump is formed.
- a spring holder is arranged within the valve cylinder and the spring holder is connected to the elastic
- the elastic valve element is disposed within the cylinder space.
- the at least one drain opening in the closed position of the closing piston is closed by the closing piston and / or the at least one drain opening opens into the opening of the closing piston in the first cylinder part space.
- a compensation opening for introducing and discharging the fluid into and out of the second cylinder subspace opens into the second cylinder subspace.
- the compensation opening serves to introduce fuel into the second Zylinderteilraum and divert.
- Closing piston changes the volume of the second Zylinderteilraumes.
- the fluid In order for any movement of the closing piston to be possible with an incompressible fuel, it is necessary for the fluid to be able to flow in and out of the second cylinder space through the compensation opening with a very small flow cross-sectional area. At the inlet opening can also pressure fluctuations occur. Such, in particular short-term, pressure fluctuations would lead to a vibration or vibration movement of the closing piston.
- a small-sized compensation opening and a, in particular complete filling of the second Zylinderteilraumes with liquid, especially fuel, thereby such vibrations or rapid reciprocating movements of the closing piston due to pressure fluctuations can be counteracted and the movement of the
- Closing piston is slow damped only due to a permanent change in pressure of the liquid at the inlet opening, so that when filling the second Zylinderteilraumes with the liquid, in particular fuel, no vibration of the closing piston and the resulting
- the at least one drain opening opens into the second cylinder part space, in particular in all positions of the
- the valve is at least partially, in particular completely, made of metal, for. As steel or aluminum, and / or plastic.
- Metal is a particularly durable and durable material for the manufacture of the valve.
- Plastic advantageously has a low weight, so that thereby the valve has a low weight.
- a plastic is one
- valve cylinder or the valve housing and / or the closing piston and / or the spring holder at least partially, in particular completely, made of plastic.
- High-pressure pump guided fuel is controlled and / or regulated with the pre-discharge pump. If the pre-demand pump can not be controlled and / or regulated in the delivery rate, this is carried out with the metering unit.
- the precharge pump comprises an electric motor.
- the electric motor of the Vorforderpumpe is integrated into the Vorforderpumpe, z. B. by permanent magnets are installed in a gear.
- the producible by the high-pressure pump pressure in the high-pressure rail is, for example, in the range of 1000 to 3000 bar z. B. for diesel engines or between 40 bar and 400 bar z. B. for gasoline engines.
- FIG. 1 shows a cross section of a high-pressure pump for conveying a fluid
- FIG. 2 shows a section A-A of FIG. 1 a roller with roller shoe and a drive shaft
- FIG. 3 is a highly schematic view of a high-pressure injection system
- Fig. 4 is a greatly simplified cross-section of the high pressure pump
- Fig. 5 is a longitudinal section of a known from the prior art
- Fig. 7 is a longitudinal section of a housing of the high pressure pump
- the overflow valve according to the invention in a recess of the housing.
- Fig. 1 is a cross section of a high-pressure pump 1 for conveying fuel is shown.
- the high-pressure pump 1 serves to fuel, z.
- the pressure which can be generated by the high-pressure pump 1 is, for example, in a range between 1000 and 3000 bar.
- the high-pressure pump 1 has a drive shaft 2 with two cams 3, which performs a rotational movement about a rotation axis 26.
- the axis of rotation 26 lies in the plane of the drawing of FIG. 1 and is perpendicular to the Drawing plane of Fig. 2.
- a piston 5 is mounted in a cylinder 6, which is formed by a housing 8.
- a working chamber 29 is bounded by the cylinder 6, the housing 8 and the piston 5.
- Into the working space 29 opens an inlet channel 22 with an inlet valve 19 and an outlet channel 24 with an outlet valve 20. Through an inlet opening at the inlet channel 22 flows
- As a check valve is designed to the effect that only fuel can flow into the working space 29 and the exhaust valve 20, z.
- B. a check valve is designed to the effect that only fuel can flow out of the working space 29.
- the volume of the working space 29 is due to an oscillating stroke of the
- Piston 5 changed.
- the piston 5 is indirectly supported on the drive shaft 2 from.
- a roller shoe 9 is attached to a roller 10.
- the roller 10 can perform a rotational movement, the axis of rotation 25 lies in the plane of FIG. 1 and is perpendicular to the plane of Fig. 2.
- the drive shaft 2 with the at least one cam 3 has a shaft rolling surface 4 and the roller 10 has a roller rolling surface 1 1.
- the roller tread 1 1 of the roller 10 rolls on a contact surface 12 on the shaft rolling surface 4 of the drive shaft 2 with the two cams 3 from.
- the roller shoe 9 is mounted in a roller shoe bearing formed by the housing 8 as a sliding bearing.
- a spring 27 or coil spring 27 as an elastic element 28 which is clamped between the housing 8 and the roller shoe 9, brings on the roller shoe 9 a compressive force, so that the roller rolling surface 1 1 of the roller 10 in constant contact with the waves Rolling surface 4 of the drive shaft 2 is.
- the roller shoe 9 and the piston 5 thus carry out together an oscillating stroke movement.
- the roller 10 is mounted with a sliding bearing 13 in the roller shoe 9.
- FIG. 3 is a highly schematic representation of a high-pressure injection system 36 for a motor vehicle not shown mapped with a high-pressure rail 30 or a fuel rail 31. From the high-pressure rail 30 and a fuel rail 31, the fuel by means of valves (not shown) in the combustion chambers (not shown) of the internal combustion engine 39 injected.
- An electric prefeed pump 35 delivers fuel from a fuel tank 32 through a fuel line 33 to the high pressure pump 1.
- the high pressure pump 1 is driven by the drive shaft 2 and the drive shaft 2 is a shaft, for. B. a crankshaft or camshaft, the
- a metering unit 37 controls and / or regulates the pro
- Time unit to the high pressure pump 1 directed volume of fuel.
- the high-pressure rail 30 serves to inject the fuel into the combustion chamber of the internal combustion engine 39.
- the fuel not required by the high-pressure pump 1 is returned to the fuel tank 32 through an optional fuel return line 34.
- Fig. 4 shows a part of the high-pressure injection system 36.
- a lubricating space 40 is formed.
- the drive shaft 2, the roller 10, the roller shoe 9 are shown (not in Fig. 4) and partially the piston 5 is arranged.
- the piston 5 By passing through the lubricant space 40 fuel these components 2, 5, 9 and 10 are lubricated by the fuel.
- a flow channel 43 is provided for this purpose, and the fuel is introduced into the lubricating space 40 through the flow channel 43 and subsequently discharged again, and after it has been discharged from the lubricating space 40 through the fuel return line
- FIG. 4 the high pressure injection system 36 shown in Fig. 3 is shown in more detail without the high pressure rail 30 and without the engine 39. This shows that
- Embodiment no metering unit 37 on.
- the prefeed pump 35 can be controlled and / or regulated in the delivery rate and is driven by an electric motor 17.
- Pre-feed pump 35 is a gear pump 14, z. Legs
- Fuel tank 32 sucked fuel is from the feed pump 35 with a prefeed pressure, z. B. 4 bar, through the fuel line 33 of the
- High pressure pump 1 supplied, ie the inlet channel 22 of the high-pressure pump 1 fed. Further, the fuel delivered by the prefeed pump 35 during operation of the engine 39 after passing through through the lubricating space 40 by a spill valve 41 and a
- Fuel return line 34 is supplied to the fuel tank 32.
- these components 2, 5, 9 and 10 can be lubricated as well as cooled.
- the overflow valve 41 is designed such that in the
- the prefeed pump 35 thereby promotes in addition to the flow rate for the high-pressure pump 1 of fuel and an additional amount of fuel for lubrication of the high-pressure pump 1, d. H. of the fuel flowing through the lubricating space 40.
- Overflow valve 41 prevails. At a pressure of less than 4.5 bar in the fuel line 33 in front of the overflow 41 closes the spill valve 41. This can be in the fuel line 33 before the spill valve 41 during operation of the engine 39 is a substantially constant feed pressure between 4.5 bar and 5.5 bar are made available, even with minor fluctuations in the delivery rate of the feed pump 35 with respect to the volume flow required by the high-pressure pump 1.
- Fig. 5 is a known from the prior art valve 42 as
- Overflow valve 41 has a valve housing 45, which has a
- Valve cylinder 44 limited. On the outside of the valve housing 45 is a
- Fixing device 38 for axial attachment within a recess 61 on the housing 8 of the high-pressure pump 1 forms. Inside the valve cylinder
- a closing piston 46 is mounted.
- the closing piston 46 can due to the Slide bearing on the valve cylinder 44 an axial movement, ie as shown in Fig. 6 from left to right and vice versa run.
- the valve cylinder 44 and the valve housing 45 include a cylinder chamber 56 a.
- the cylinder chamber 56 is subdivided by the closing piston 46 into a first cylinder subspace 57 and a second cylinder subspace 58.
- In the first cylinder part space 57 opens an inlet opening 47 for fluid, in particular fuel, since in the valve housing 45 an inlet channel 48 is incorporated.
- the inlet channel 48 is formed in the axial direction in the valve housing 45.
- two drainage openings 49 open into the first cylinder part space 57, because two radial discharge passages 50 are incorporated into the valve housing 45.
- the closing piston 46 or the cap 46 is at an axial portion with a larger diameter or radius by means of a sliding bearing on the
- Valve cylinder 44 stored. At a second section, the
- Closing piston 46 has a smaller diameter and in the right end of this portion with the smaller diameter, the closing piston 46 has a sealing seat 54.
- a valve spring 52 is elastic
- Valve element 51 is arranged.
- the elastic valve element 51 is attached at one end to a fixed spring holder 53 and at another end to the closing piston 46.
- the spring holder 53 closes the valve cylinder 44 and is formed as a separate component in addition to the valve housing 45. Notwithstanding this, the spring holder 53 also integrally with the
- Valve housing 45 may be formed (not shown). On the outside, 45 two sealing grooves 62 are formed on the valve housing, in each of which a
- Sealing ring 63, z. B. an elastic rubber seal is arranged.
- the housing 8 of the high-pressure pump 1 has a correspondingly complementary design
- a partial opening position of the closing piston 46 is shown.
- the two drain openings 49 are partially closed by the portion of the closing piston 46 with the larger diameter and partly, the fluid can flow out of the first cylinder subspace 57 through the two drainage openings 49.
- the fluid in particular the fuel, flows through the inlet channel 48 into the first cylinder subspace 57.
- Increases the pressure of the fuel in the first cylinder part space 57 on, z. B. to a value of more than 5 bar moves due to the greater pressure of the fuel in the first cylinder part space 57 of the closing piston 46 against the force applied by the valve spring 52 compressive force further to the left, so that thereby the two flow channels 50 are opened further.
- the closing piston 46 moves to the right until the sealing seat 54 completely closes the inlet channel 48 or the inlet opening 47 opening into the first cylinder-part space 57.
- the volume of the second also changes
- Cylinder part space 58 There is little play between the closing piston 46 with the section with the larger diameter and the valve cylinder 44, so that fuel also passes from the first cylinder subspace 57 into the second cylinder subspace 58 to a very small extent.
- the second cylinder part space 58 is thus, if the second cylinder part space 58 or
- Spring chamber 58 is not filled with air is due to a low pressure in the fuel return line 34, filled with the substantially incompressible fuel. In order to allow a movement of the closing piston 46 at all, it is necessary that the fuel located in the second cylinder part space 58 through a compensation opening 59 from the second
- Cylinder part space 58 can be passed to the outside and back to the inside.
- the compensation opening 59 has a very small diameter or a small flow cross-sectional area, for. B. a diameter in the range between 0.5 mm and 1 mm. Pressure fluctuations of the fuel in the region of the inlet opening 47 do not cause a vibration of the
- the sealing seat 54 advantageously allows a complete sealing of the overflow valve 41 in the closed position of the closing piston 46.
- FIG. 6 shows a longitudinal section of an overflow valve 41 according to the invention.
- the valve housing 45 has on the outside no thread 60 as a fixing device 38 for the axial attachment of the valve housing 45 to a housing 8 of the high-pressure pump 1.
- Overflow valve 41 can thus not in the axial direction, that is, in the direction of a longitudinal axis 77 of the valve 42 and a longitudinal axis 77 formed as a bore 64 recess 61 on the housing 8 of the high pressure pump (Fig. 7) are fixed in the axial direction.
- a longitudinal axis 77 of the valve 42 and a longitudinal axis 77 formed as a bore 64 recess 61 on the housing 8 of the high pressure pump (Fig. 7) are fixed in the axial direction.
- the sealing ring 63 is located on the sealing groove 62 of the valve housing 45 on a shoulder 78 on the housing 8 of the high pressure pump 1 (Fig. 7).
- the valve 42 has a first inner end 72 and a second outer end 73. On the second outer end 73 of the spill valve 41 is formed as a return pipe 69 nozzle 68. The nozzle 68 is connected by means of a press bond 71 fluid-tight and non-positively connected to the housing 8 of the high-pressure pump 1.
- the bore 64 has a first inner end 65 and a second outer end 66. Due to the resting of the second outer end 73 of the
- Overflow valve 41 has only between the two drain openings 49 and the inlet opening 47 at the first inner end 72 of the spill valve 41 the
- Radialstutzennuten 76 is formed so that the fuel flowing through the gap 74 in the region of the second outer end 73 of the
- Overflow valve 41 can flow through these Radialstutzennuten 76 in the radial direction to a nozzle channel 70. Due to the sectional formation in Fig. 7, only one of the plurality of Radialstutzennutzen 76 is visible.
- the annular Gap 74 is additionally subdivided into a fictitious partial gap 75 and the partial gap 75 begins in the axial direction at the
- the fuel is discharged from the lubricant chamber 40 and through the nozzle channel 70, the fuel through the nozzle channel 70 as the flow channel 43 of the
- Fuel return line 34 is supplied.
- the fuel return line 34 (not shown in FIG. 7) is attached to the outer end of the nozzle 68.
- the fuel flows through an orifice 79 of the recess inlet channel 67 in the
- the fuel return line 34 has no constriction or no back pressure, so that when a high-pressure pump 1 and a
- the fuel return line 34 and thus also the nozzle channel 70 and the gap 74 of fuel runs empty, that is filled with air.
- the prefeed pump 35 is designed in terms of delivery that in normal operation, the closing piston 46 is slightly opened to ensure cooling of the components within the lubricating space 40.
- the intermediate space 74 of fuel constantly flows through and thereby also the nozzle channel 70, so that an air volume possibly present in the
- Gap 74 and the nozzle channel 70 is immediately filled with fuel and thereby the air is removed from the gap 74 in a very short time after starting the prefeed pump 35 and the high-pressure pump 1.
- the spring chamber 58 and the second cylinder part space 58 is in fluid-conducting connection with the compensation opening 49 with the intermediate space 74 or the
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE201310201892 DE102013201892A1 (en) | 2013-02-06 | 2013-02-06 | Valve |
PCT/EP2013/076667 WO2014121870A1 (en) | 2013-02-06 | 2013-12-16 | Valve |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2954192A1 true EP2954192A1 (en) | 2015-12-16 |
EP2954192B1 EP2954192B1 (en) | 2017-10-25 |
Family
ID=49911493
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13815445.5A Active EP2954192B1 (en) | 2013-02-06 | 2013-12-16 | High pressure pump |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2954192B1 (en) |
CN (1) | CN104981605B (en) |
DE (1) | DE102013201892A1 (en) |
WO (1) | WO2014121870A1 (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105464863A (en) * | 2015-12-09 | 2016-04-06 | 中国船舶重工集团公司第七一一研究所 | Electronic unit pump system and oil spray control method |
GB201602013D0 (en) * | 2016-02-04 | 2016-03-23 | Delphi Internat Operations Luxembourg S À R L | High pressure diesel fuel pump |
CN107762691A (en) * | 2017-09-19 | 2018-03-06 | 北汽福田汽车股份有限公司 | Pipe connecting component and vehicle |
GB2570648B (en) * | 2018-01-26 | 2020-10-14 | Delphi Tech Ip Ltd | Fuel Pump |
DE102019203967A1 (en) * | 2018-03-27 | 2019-10-02 | Keihin Corporation | VALVE UNIT FASTENING STRUCTURE AND FLUID PUMP WHICH USES SELF |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007052665A1 (en) * | 2007-11-05 | 2009-05-07 | Robert Bosch Gmbh | Fuel overflow valve for a fuel injector and fuel injector with fuel spill valve |
ITMI20072219A1 (en) * | 2007-11-23 | 2009-05-24 | Bosch Gmbh Robert | OVERPRESSURE VALVE AND HIGH PRESSURE PUMP INCLUDING THIS PRESSURE VALVE |
JP4518140B2 (en) * | 2007-12-05 | 2010-08-04 | 株式会社デンソー | Fuel supply device |
JP4968037B2 (en) * | 2007-12-13 | 2012-07-04 | 株式会社デンソー | Back pressure control valve and low pressure fuel system using the same |
DE102009026596A1 (en) | 2009-05-29 | 2010-12-02 | Robert Bosch Gmbh | High-pressure pump for high pressure injection system for internal combustion engine, particularly for motor vehicle, has drive shaft with cam, piston and cylinder |
DE102009027146A1 (en) * | 2009-06-24 | 2010-12-30 | Robert Bosch Gmbh | Fuel high-pressure pump for fuel system of internal combustion engine, has suction side low pressure area, in which overflow valve is arranged, where overflow valve has valve housing with inlet, outlet, valve body and valve spring |
ITMI20110582A1 (en) * | 2011-04-08 | 2012-10-09 | Bosch Gmbh Robert | PUMPING GROUP FOR FOOD FUEL, PREFERIBLY GASOIL, FROM A CONTAINMENT TANK TO AN INTERNAL COMBUSTION ENGINE |
DE102012200894A1 (en) * | 2012-01-23 | 2013-07-25 | Robert Bosch Gmbh | High-pressure fuel pump of an injection system |
-
2013
- 2013-02-06 DE DE201310201892 patent/DE102013201892A1/en not_active Withdrawn
- 2013-12-16 EP EP13815445.5A patent/EP2954192B1/en active Active
- 2013-12-16 CN CN201380072317.XA patent/CN104981605B/en active Active
- 2013-12-16 WO PCT/EP2013/076667 patent/WO2014121870A1/en active Application Filing
Non-Patent Citations (1)
Title |
---|
See references of WO2014121870A1 * |
Also Published As
Publication number | Publication date |
---|---|
CN104981605B (en) | 2018-06-08 |
CN104981605A (en) | 2015-10-14 |
WO2014121870A1 (en) | 2014-08-14 |
EP2954192B1 (en) | 2017-10-25 |
DE102013201892A1 (en) | 2014-08-07 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE102011055964B4 (en) | fuel feed pump | |
WO2013124103A1 (en) | High-pressure pump | |
EP2954192B1 (en) | High pressure pump | |
EP2935857B1 (en) | High pressure injection system | |
DE102011086692A1 (en) | Valve i.e. overflow valve, for use in common-rail injection system for e.g. diesel engine of motor car, has inlet apertures supplying fluid within cylinder space, where one of apertures is closed and opened in closing and opening positions | |
EP3014107B1 (en) | Pumping device, in particular high pressure fuel pumping device for a fuel injection device | |
DE102011076023A1 (en) | Valve for high-pressure injection system for internal combustion engine, particularly for motor vehicle, has valve cylinder and closing piston movable within valve cylinder between closing position and open position | |
WO2017071867A1 (en) | High-pressure pump | |
EP2809943B1 (en) | High-pressure pump | |
EP1394403B1 (en) | Fuel system for an internal combustion engine | |
EP2872771B1 (en) | High-pressure pump | |
DE102012212154A1 (en) | High pressure pump for conveying fluid e.g. diesel, in common-rail-injection system of diesel engine of motor vehicle, has shaft comprising recess such that channel discharging fluid from lubricating area is formed between shaft and bearing | |
EP2673495A1 (en) | High pressure pump | |
DE102006000832B4 (en) | Radial piston pump with flow control | |
EP2850318B1 (en) | High pressure pump | |
DE102017218730A1 (en) | High-pressure fuel pump | |
EP2872778B1 (en) | High-pressure pump | |
DE102012201308A1 (en) | High-pressure pump for delivering fluid e.g. diesel to diesel engine, has elastic sealing element to seal connecting unit for connecting closure element and piston carrier, with respect to inlet and outlet channels | |
DE102012202718A1 (en) | Valve e.g. overflow valve of high pressure injection system e.g. common-rail injection system for motor car, has compressive force applying unit that is provided with permanent magnets for applying compressive force on closing piston | |
DE10205495A1 (en) | Fuel pump, for internal combustion engine with direct fuel injection, has housing with drive shaft, at least one bearing section, one drive section and first recess in which section and drive section of drive shaft are accommodated | |
DE102012202717A1 (en) | High pressure pump for use in common-rail injection system to convey e.g. diesel to diesel engine of motor car, has working chamber comprising dead volume that is narrowed by additional insert in addition to housing | |
DE102011086690A1 (en) | Operating system for high pressure injection system for e.g. diesel engine of motor car, has valve housing of overflow valve and measuring housing of measuring unit, which are formed integrally | |
DE102009026717A1 (en) | High-pressure fuel pump for fuel injection system of internal combustion engine, has pump housing, in which drive shaft is supported by bearings, through which fuel is forced for lubrication or cooling | |
DE102011076057A1 (en) | Method for operating common-rail injection system for injecting e.g. petrol into combustion chamber of petrol engine of motor car, involves conveying fuel from feed pump to high pressure rail before starting of engine |
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: 20150907 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
DAX | Request for extension of the european patent (deleted) | ||
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20170504 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 940202 Country of ref document: AT Kind code of ref document: T Effective date: 20171115 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502013008679 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 5 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20171025 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL 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: 20171025 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20171025 Ref country code: NO 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: 20180125 Ref country code: SE 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: 20171025 Ref country code: FI 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: 20171025 Ref country code: LT 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: 20171025 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LV 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: 20171025 Ref country code: HR 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: 20171025 Ref country code: IS 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: 20180225 Ref country code: GR 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: 20180126 Ref country code: BG 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: 20180125 Ref country code: RS 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: 20171025 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502013008679 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CZ 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: 20171025 Ref country code: DK 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: 20171025 Ref country code: CY 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: 20171025 Ref country code: EE 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: 20171025 Ref country code: SK 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: 20171025 |
|
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: RO 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: 20171025 Ref country code: PL 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: 20171025 Ref country code: SM 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: 20171025 |
|
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 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20180125 |
|
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: 20171216 Ref country code: MT 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: 20171025 |
|
26N | No opposition filed |
Effective date: 20180726 |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20171231 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171216 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171231 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180125 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171231 Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171231 Ref country code: SI 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: 20171025 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20131216 Ref country code: MC 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: 20171025 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK 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: 20171025 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 940202 Country of ref document: AT Kind code of ref document: T Effective date: 20181216 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR 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: 20171025 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20181216 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PT 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: 20171025 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AL 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: 20171025 |
|
P01 | Opt-out of the competence of the unified patent court (upc) registered |
Effective date: 20230509 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20231219 Year of fee payment: 11 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20240227 Year of fee payment: 11 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20231229 Year of fee payment: 11 |