EP2932086A1 - Pumpenanordnung und system für ein kraftfahrzeug - Google Patents
Pumpenanordnung und system für ein kraftfahrzeugInfo
- Publication number
- EP2932086A1 EP2932086A1 EP14749845.5A EP14749845A EP2932086A1 EP 2932086 A1 EP2932086 A1 EP 2932086A1 EP 14749845 A EP14749845 A EP 14749845A EP 2932086 A1 EP2932086 A1 EP 2932086A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- relief valve
- pump
- valve
- opening
- 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 78
- 238000002485 combustion reaction Methods 0.000 claims description 6
- 230000000712 assembly Effects 0.000 claims 2
- 238000000429 assembly Methods 0.000 claims 2
- 230000010349 pulsation Effects 0.000 description 9
- 239000000446 fuel Substances 0.000 description 8
- 238000002347 injection Methods 0.000 description 8
- 239000007924 injection Substances 0.000 description 8
- 238000007789 sealing Methods 0.000 description 7
- 238000007639 printing Methods 0.000 description 6
- 238000004891 communication Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 239000008141 laxative Substances 0.000 description 1
- 230000002475 laxative effect Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
- F02D1/02—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered
- F02D1/06—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered by means dependent on pressure of engine working fluid
-
- 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
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
- F02M63/023—Means for varying pressure in common rails
- F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
- F02M63/0245—Means for varying pressure in common rails by bleeding fuel pressure between the high pressure pump and the common rail
-
- 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
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
- F02M55/025—Common rails
-
- 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
- F02M59/025—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 a single piston
-
- 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
-
- 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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
-
- 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
- F02M63/0012—Valves
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/005—Pressure relief valves
-
- 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
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0205—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine
- F02M63/0215—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine by draining or closing fuel conduits
-
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/18—Fuel-injection apparatus having means for maintaining safety not otherwise provided for
-
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/24—Fuel-injection apparatus with sensors
- F02M2200/247—Pressure sensors
-
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
- F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
-
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
- F02M2200/8092—Fuel injection apparatus manufacture, repair or assembly adjusting or calibration
Definitions
- the invention relates to a pump arrangement for a motor vehicle. Furthermore, the invention relates to a system with a pump assembly for a motor vehicle, in particular a fuel injection system.
- Pumps for fluid delivery in particular a pump for the ⁇ fuel delivery for an injection system of a motor vehicle, conventionally have a pressure relief valve. This valve is located on the high pressure side of the pump. The valve is designed in such a way that, in the event of a fault, the maximum volume flow conveyed by the high-pressure pump can be returned to the high-pressure piston space of the pump. This protects the high-pressure system with the pump from impermissibly high pressures. Under normal operating conditions, the valve is closed.
- the valve can only during the suction phase of the pump öff ⁇ NEN. During the compression phase of the pump the valve is locked hydrau ⁇ lisch and can not open. It is desirable to provide a pump assembly for a motor vehicle that enables reliable operation. It is further desirable to provide a system in a pump assembly that allows reliable operation.
- the invention relates to a pump assembly for a motor vehicle and a system comprising such a pump assembly.
- the pump arrangement has a high pressure pump for delivering a
- the high-pressure pump has a fluid inlet and a fluid outlet and a pressure chamber, which is arranged hydraulically between the fluid inlet and the fluid outlet.
- the pump arrangement has a first pressure limiting valve, which is coupled on the input side with the fluid outlet.
- the pump arrangement has a second pressure relief valve.
- the two pressure relief valves are hydraulically connected in parallel.
- the two pressure relief valves each have an opening pressure.
- the value of the opening pressure of the first pressure limiting valve is greater than the value of the opening pressure of the second pressure limiting valve.
- the pump arrangement can be coupled hydraulically with an injector.
- the value of the opening pressure of the second pressure relief valve is predetermined as a function of the injector.
- the first pressure relief valve is in particular si ⁇ cherines that the maximum allowable pressure at the fluid outlet of the high-pressure pump is not exceeded.
- the value of the opening pressure of the first pressure relief valve is in particular greater than the normal operating auftre ⁇ border system pressures in the pressure phase of the high-pressure pump.
- the first pressure limiting valve does not open in normal operation. In the event of a fault, the first pressure relief valve protects against excessive pressures.
- the second pressure limiting valve ensures reliable opening of the injectors which can be coupled to the pump arrangement.
- the value of the opening pressure of the second pressure relief valve is set so that the value of the opening pressure below the highest allowable pressure for the injector is located. This ensures the function of the injectors. Under the highest allowable pressure for the injector is to be understood as the fluid pressure at which the injector can just open reliably.
- the second Druckbegren ⁇ relief valve permits an opening in each intake phase of the high-pressure pump to dampen pressure pulsations occurring. This makes it possible to protect the first pressure relief valve before Ver ⁇ wear since the first pressure relief valve remains closed during normal operation and in case of error öff ⁇ net.
- the first pressure limiting valve is hydraulically coupled to the fluid inlet on the output side. This makes it possible, in the event of a fault, during the printing phase of the high pressure pump to open the first pressure relief valve. A hydraulically sealed pressure relief valve is thus avoidable.
- the first pressure relief valve is designed so that the maximum volume flow of the high pressure pump through the first pressure relief valve is laxative bar. Thus, by the first pressure relief valve during the entire cycle of the high-pressure pump ensures that the maximum allowable pressure in the fluid flow is not exceeded. If an error occurs, it is possible that the whole supported by the high-pressure pump maximum Volu ⁇ volume flow is discharged back into the low pressure area at the fluid inlet without any significant increase in pressure. An inadmissible pressure increase during the printing phase is avoided.
- the second pressure limiting valve is hydraulically coupled to the pressure chamber on the output side. Because of ⁇ is a hydraulic closure of the second Druckbe- limit valve during the pressure phase of the high pressure pump possible. Thus, a good efficiency of the pump is achieved, since the entire volume of a pumping cycle for fluid flow is ge ⁇ promotes. By the first pressure relief valve, the pump assembly is always protected against unacceptably high pressures.
- the second pressure relief valve is hydraulically coupled to the fluid inlet on the output side.
- the second relief valve ⁇ Druckbe is input is coupled to the fluid flow.
- a hydraulic communication between the fluid ⁇ drain and the fluid inlet with an open second Druckbe ⁇ relief valve is possible.
- the two ⁇ te pressure relief valve opens during each printing stage.
- pressure pulsations on the fluid drain are minimized.
- the dead volume within the high-pressure pump is reduced, where ⁇ is effected by an increase in efficiency.
- the second pressure relief valve is coupled on the input side to the pressure chamber.
- a hydraulic communication between the pressure chamber and the fluid inlet is possible with open second pressure relief ⁇ valve. This makes it possible to minimize pressure pulsations in the pressure chamber and the fluid drain.
- the second pressure relief valve can open in each pressure phase of the high pressure pump.
- the second pressure limiting valve is designed as a passive pressure control valve with firmly set ⁇ opening pressure.
- the system pressure is set to the value of Opening pressure of the second pressure relief valve raised. Because the opening pressure is fixed, the value of the opening pressure can be used as a reference.
- the fluid drain can be coupled to a high-pressure manifold. With the high-pressure manifold the injector can be coupled.
- the value of the opening pressure of the first pressure relief valve is insbeson ⁇ particular ben vorgege- a function of the high-pressure manifold. The value of the opening pressure is particularly so specified differently that a maximum set pressure for the high pressure manifold is not exceeded.
- the value of the opening pressure of the second pressure limiting valve is in particular dependent on the lowest
- FIG. 1 shows a schematic representation of a fuel injection system according to embodiments
- FIG. 2 shows a schematic illustration of a fuel injection system according to embodiments
- FIG. 3 shows a schematic representation of a fuel injection system according to embodiments
- FIG. 4 shows a schematic detail view of a pump arrangement according to embodiments
- FIG. 1 shows a pump arrangement 100.
- the pump arrangement 100 is particularly part of a fuel injection system of a motor vehicle.
- the fuel injection system is in particular ⁇ a so-called common rail injection system.
- the pump arrangement 100 has a high-pressure pump 101 with a fluid inlet 102 and a fluid outlet 103. Hydraulically between the fluid inlet 102 and the fluid outlet 103, a pressure chamber 104 is provided.
- the fluid inlet 102 is arranged on a low-pressure side 114.
- the fluid inlet 102 serves in particular for coupling the pressure chamber 104 with a fluid tank 113.
- the fluid outlet 103 is provided on a high-pressure side 115.
- the Fluidab ⁇ run 103 is particularly coupled to a high pressure manifold 112th With the high pressure manifold injectors is a gate 107, respectively, a plurality of injectors 107 gekop ⁇ pelt.
- the injectors are designed to operate
- the fluid is conveyed from the fluid tank 113 and conveyed to the high-pressure manifold 112 under pressure.
- On the low pressure side 114 prevail in operation, for example, pressures of less than 5 bar.
- On the high-pressure side 115 and in particular in the fuel manifold 112 especially see pressures of over 300 bar, for example 350 bar or more.
- the high-pressure pump 101 is in particular a piston pump.
- a piston 122 is arranged in the pressure chamber 104. Moves the piston 121 along its longitudinal axis so that the volume of the pressure chamber 104 increases, fluid is through the
- the pump arrangement 100 has a first pressure limiting valve 105.
- An input side 108 of the Druckbegrenzungsven ⁇ tils 105 is hydraulically connected to the fluid drain 103.
- An output side 110 of the first pressure relief valve 105 is hydraulically connected to the fluid inlet 102.
- the input side 108 of the first pressure relief valve 105 is hydraulically coupled to the high pressure side 115.
- the output ⁇ side 110 of the first pressure relief valve 105 is hydraulically coupled to the low pressure side 114.
- the first pressure relief valve 105 has a predetermined opening pressure.
- the pressure limiting valve 105 blocks ei ⁇ nen fluid flow through the pressure relief valve 105 at Drü ⁇ bridges below the predetermined opening pressure. At pressures from the predetermined opening pressure, the pressure limiting valve 105 releases a fluid flow through the pressure limiting valve 105.
- the value of the opening pressure of the first Druckbegren ⁇ limiting valve 105 is set so that a predetermined ma ⁇ ximaler pressure in the fluid flow 103, and in particular in the high-pressure manifold 112 is not exceeded.
- the first te pressure relief valve 105 is closed during normal operation of Pum ⁇ penanssen 100.
- the first pressure relief valve 105 When the predetermined value of the opening pressure at the input side 108 is reached and / or exceeded, the first pressure relief valve 105 opens and releases a fluid flow from the input side 108 to the output side 110. Thus, the pressure on the high ⁇ pressure side 115 is kept within predetermined limits. Characterized in that the first pressure relief valve 105 is hydraulically connected to the fluid inlet 102, it is possible that the first pressure relief valve 105 opens both during the suction phase of the high pressure pump 101 and during the pressure phase of the high pressure pump 101. The first
- Pressure relief valve 105 is not hydraulically locked.
- the pump arrangement 100 has a second pressure- limiting valve 106.
- the second pressure relief valve 106 is in particular a passive pressure control valve.
- the second pressure ⁇ limiting valve 106 has an opening pressure whose value is predetermined.
- the second pressure relief valve 106 has a predetermined opening pressure.
- the pressure relief valve 106 blocks fluid flow through the relief valve 106 Druckbe ⁇ at pressures below the predetermined opening pressure. At pressures from the predetermined opening pressure, the pressure limiting valve 106 releases a fluid flow through the pressure limiting valve 106.
- the value of the opening pressure of the second pressure limiting valve is smaller than the value of the opening pressure of the first pressure limiting valve.
- An exit side 111 of the second printing limit valve 106 is hydraulically coupled to the pressure chamber 104.
- the second pressure relief valve 106 is hydraulically locked according to the embodiments, as shown in Figure 1, during the pressure phase of the high pressure pump 101.
- the second pressure limiting valve 106 can open only during the suction phase of the high-pressure pump 101 and is always closed during a pressure phase of the high-pressure pump 101.
- the value of the opening pressure of the second pressure-limiting valve is predetermined in particular as a function of the injector 107.
- the value of the opening pressure of the second pressure limiting valve 106 is predetermined as a function of the highest permissible Injektorö Maschinensdrucks. Characterized a verläss ⁇ Licher operation of the injectors 107 is made possible.
- the value of the opening pressure of the second pressure relief valve 106 is below the maximum admissible pressure of the In ⁇ jektors 107.
- the function of the injector 107 si ⁇ cherines, so a reliable opening and injecting fluid into the combustion chamber.
- the use of a passive pressure control valve with specified differently benem value of the opening pressure also allows calibra tion ⁇ a pressure sensor 123.
- the pressure sensor 123 is Scheme- directed to determine the fluid pressure in the high-pressure manifold 112.
- the predetermined value of the opening pressure of the two ⁇ th pressure relief valve 106 is not changed during operation in particular. This makes it possible, the pressure sensor 123 against the fixed referenced value of the opening pressure of the second pressure relief valve 106 to calib ⁇ Center.
- This is not possible with a conventionally employed actively controlled pressure control valve, since the Publ ⁇ design pressure can be controlled at ⁇ an active valve through the applied control voltage to different values of the opening pressure and thus can not form a fixed reference.
- the use of the passive second pressure relief valve 106 is also less expensive than a commonly used active pressure control valve.
- the second pressure relief valve 106 serves as a pressure relief valve to ensure the highest allowable pressure at the injector 107.
- the pressure relief valve 106 serves as a pressure regulating valve to minimize pressure pulsations and in particular to perform the calibration of the pressure sensor 123.
- the cross-sections of the second Druckbe ⁇ grenzungsventils 106 are particularly so given that a maximum surface pressure bridge despite high Fluiddrü- is not exceeded.
- the second pressure limiting valve 106 is designed in particular durable.
- the value of the opening pressure of the first pressure relief valve 105 is so high that pressure pulsations during loading ⁇ drive the pump assembly 100 does not lead to the opening of the first pressure relief valve 105th
- the first Druckbegren ⁇ relief valve 105 is connected to its output side 110 with the Never ⁇ dertik Colour 114th As a result, a pressure reduction is independent of the suction phase and the pressure phase of the high-pressure pump 101 possible. Thus, it is avoided that during the pressure phase, the pressures in the line are greater than the value of the opening pressure of the first pressure relief valve 105, which may occur during hydraulically interlocked pressure relief valves during the pressure phase.
- the cross sections of the first pressure relief valve 105 are predetermined so that at maximum flow from the high pressure pump 101, the maximum allowable system pressure is not exceeded in case of failure.
- the first pressure limiting valve 105 is designed for larger volume flows than the second pressure limiting valve 106.
- the value of the opening pressure of the first in over-pressure limiting valve is above the 105 occur during normal operation ⁇ the system pressures in the compression phase fixed.
- the value of the second pressure limiting valve 106 is set lower than the value of the opening pressure of the first pressure limiting valve 105.
- FIG. 2 shows the pump arrangement 100 according to further embodiments.
- the pump arrangement 100 of FIG. 2 substantially corresponds to the embodiments of the pump arrangement 100 as explained in connection with FIG.
- the output side 111 of the second pressure relief valve 106 is hydraulically connected to the fluid inlet 102.
- the second pressure relief valve 106 is the output side connected to the low pressure side 114 hydraulically. Thus, when the second pressure relief valve 106 is open, a fluid flow from the fluid outlet 103 into the low pressure region 114 is possible.
- the second pressure limiting valve 106 is not hydraulically closed during the pressure phase of the high-pressure pump 101. Thus, it is possible that the second pressure- limiting valve 106 öff ⁇ net during the printing phase of the high-pressure pump 101. As a result, pressure pulsations in the fluid outlet 103 and in the high-pressure manifold 112 are minimized by the second pressure-limiting valve 106.
- the dead volume within the high-pressure pump 101 is reduced. This causes We ⁇ ciency increase of the pump assembly 100th
- FIG. 3 shows the pump arrangement 100 according to further embodiments.
- the pump arrangement 100 according to FIG. 3 essentially corresponds to the embodiments as explained in connection with FIGS. 1 and 2.
- the input side 109 of the second pressure relief valve 106 is hydraulically connected to the pressure chamber 104th
- the output side 111 of the second pressure relief valve 106 is hydraulically connected to the fluid inlet 102 be ⁇ relationship as the low pressure side 114th
- With an open second pressure relief valve 106 a fluid flow from the pressure chamber 104 in the fluid supply 102 is released ⁇ .
- the second pressure relief valve 106 opens during each pressure phase of the high-pressure pump 101. Pressure pulsations in the fluid outlet 103, in the high-pressure manifold 112 and in the pressure chamber 104 are thus minimized.
- FIG. 4 shows the first pressure-limiting valve 105 and the second pressure-limiting valve 106, which are connected in parallel hydraulically. The value of the opening pressure of the first
- the first pressure relief valve 105 is designed for larger Vo ⁇ lumenströme than the second pressure relief valve 106.
- the value of the opening pressure and the value of the maximum volume flow of the first pressure relief valve 105 are so predetermined in that a maximum predetermined pressure in the high-pressure region 115 is never exceeded when the first pressure-limiting valve 105 is functioning.
- the value of the opening pressure and the value of the maximum volume flow of the second pressure limiting valve 106 are predetermined such that a safe opening of the injectors 107 is ensured, as well as pressure pulsations are damped.
- Figure 5 shows a schematic representation of the second
- the second pressure limiting valve 106 is designed differently according to further embodiments .
- the second pressure relief valve 106 is a so-called passive pressure control valve.
- the second pressure relief valve 106 has a housing 120. In the housing, a spring 116 between a holding member 119 and a sealing element 117th biased. The sealing element 117 is pressed by the spring against a sealing seat 118. The sealing seat is disposed between the input 109 and the output 110. If the pressure on the input side 109 increases, the sealing element 117 is moved away from the sealing seat 118 against the spring force of the spring 116 and a fluid flow is released from the input side 109 to the output side 110.
- a tapered cross-section 121 which serves to limit the flow.
- the value of the opening pressure of the second pressure limiting valve 106 is predetermined by the bias of the spring 116.
- the bias of the spring 116 is adjusted. If the bias voltage 116 reaches a predetermined value, the position of the holding element 119 relative to the housing 120 is fixed.
- the value of the opening pressure of the second pressure relief valve 106 is thus easily vorgeb ⁇ bar. Due to the limiting cross-section 121, a flow limitation is realized with the valve open. In addition, simply a stroke stop for the sealing element 117 is realized.
- the second pressure relief valve 106 is formed according to embodiments ⁇ forms as a so-called cartridge valve, ie as an independent component.
- the second pressure limiting valve 106 is designed according to embodiments as a so-called plug-in valve, ie as a plug-in component.
- the second Druckbe ⁇ relief valve 106 is incorporated in accordance with embodiments directly into a housing of the pump one hundred and first
- first and second pressure relief valves 105, 106 in the pump assembly 100, it is possible to reduce the pressure on the high pressure side 115 during operation as compared to conventional systems. Thus, it is possible to have a low-cost O-ring seal between the High-pressure manifold 112 and the injector 107 to provide. Thus, can be dispensed with expensive metal seals. With the combination of the two pressure relief valves 105, 106, it is possible at a pressure on the high pressure side 115 of up to 350 bar a low-emission operation of
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102013216817.9A DE102013216817A1 (de) | 2013-08-23 | 2013-08-23 | Pumpenanordnung und System für ein Kraftfahrzeug |
PCT/EP2014/067144 WO2015024804A1 (de) | 2013-08-23 | 2014-08-11 | Pumpenanordnung und system für ein kraftfahrzeug |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2932086A1 true EP2932086A1 (de) | 2015-10-21 |
EP2932086B1 EP2932086B1 (de) | 2017-06-07 |
Family
ID=51300765
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14749845.5A Active EP2932086B1 (de) | 2013-08-23 | 2014-08-11 | Pumpenanordnung und system für ein kraftfahrzeug |
Country Status (7)
Country | Link |
---|---|
US (1) | US20160153366A1 (de) |
EP (1) | EP2932086B1 (de) |
JP (1) | JP6161731B2 (de) |
KR (1) | KR101857376B1 (de) |
CN (1) | CN104956066B (de) |
DE (1) | DE102013216817A1 (de) |
WO (1) | WO2015024804A1 (de) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20160281275A1 (en) | 2015-03-26 | 2016-09-29 | Sanko Tekstil Isletmeleri San. Ve Tic. A.S. | Elastic fabric and process of preparation |
DE102015215688B4 (de) * | 2015-08-18 | 2017-10-05 | Continental Automotive Gmbh | Ansteuerverfahren zum Ansteuern eines Kraftstoffeinspritzsystems sowie Kraftstoffeinspritzsystem |
FR3079882B1 (fr) | 2018-04-10 | 2020-10-16 | Continental Automotive France | Procede de surveillance d'un capteur de pression dans un systeme d'injection directe |
CN109441685B (zh) * | 2018-10-29 | 2023-09-22 | 中船动力研究院有限公司 | 船用低速机高压共轨系统 |
DE102019212247A1 (de) * | 2019-08-15 | 2021-02-18 | Robert Bosch Gmbh | Kraftstoff-Hochdruckpumpe |
CN110671224A (zh) * | 2019-11-08 | 2020-01-10 | 重庆红江机械有限责任公司 | 一种具有多重安保功能的低速机高压共轨系统 |
Family Cites Families (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3939779B2 (ja) * | 1995-05-26 | 2007-07-04 | ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング | 内燃機関の燃料供給のための燃料供給装置 |
JPH11200990A (ja) * | 1998-01-07 | 1999-07-27 | Unisia Jecs Corp | 燃料噴射制御装置 |
EP1411238B1 (de) * | 2002-10-15 | 2006-01-11 | Robert Bosch Gmbh | Druckbegrenzungsventil für ein Kraftstoffeinspritzsystem |
DE102004009792B3 (de) * | 2004-02-28 | 2005-09-22 | Daimlerchrysler Ag | Kraftstoffzuführeinrichtung zur Versorgung der Injektoren an Brennräumen einer Brennkraftmaschine mit Kraftstoff |
DE102004013307B4 (de) * | 2004-03-17 | 2012-12-06 | Robert Bosch Gmbh | Kraftstoffhochdruckpumpe mit einem Druckbegrenzungsventil |
DE102005033638A1 (de) * | 2005-07-19 | 2007-01-25 | Robert Bosch Gmbh | Kraftstoff-Fördereinrichtung, insbesondere für eine Brennkraftmaschine |
JP4415929B2 (ja) * | 2005-11-16 | 2010-02-17 | 株式会社日立製作所 | 高圧燃料供給ポンプ |
DE102007010502A1 (de) * | 2007-03-05 | 2008-09-11 | Robert Bosch Gmbh | Kraftstoffhochdruckpumpe für eine Brennkraftmaschine mit Druckausgleichseinrichtung |
JP5196321B2 (ja) * | 2008-12-26 | 2013-05-15 | 株式会社デンソー | 燃料供給装置、及び、高圧ポンプ |
DE102009028116A1 (de) * | 2009-07-30 | 2011-02-03 | Robert Bosch Gmbh | Kraftstoffhochdruckpumpe mit einem Druckbegrenzungsventil |
DE102010031628A1 (de) * | 2009-08-17 | 2011-02-24 | Robert Bosch Gmbh | Kraftstofffördereinrichtung für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine |
JP2011132941A (ja) * | 2009-11-26 | 2011-07-07 | Nippon Soken Inc | 圧力制御弁 |
JP5529615B2 (ja) * | 2010-04-08 | 2014-06-25 | 株式会社デンソー | 高圧ポンプ |
DE102010027858A1 (de) * | 2010-04-16 | 2011-11-24 | Robert Bosch Gmbh | Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine |
JP5158219B2 (ja) * | 2010-06-29 | 2013-03-06 | 株式会社デンソー | リリーフ弁及びこれを用いた高圧ポンプ |
DE102010064192A1 (de) * | 2010-12-27 | 2012-06-28 | Robert Bosch Gmbh | Druck-Schaltventil für ein Kraftstoffeinspritzsystem einer Brennkraftmaschine |
DE102010064171A1 (de) * | 2010-12-27 | 2012-06-28 | Robert Bosch Gmbh | Druckregelanordnung eines Kraftstoffversorgungssystems |
JP5501272B2 (ja) * | 2011-03-08 | 2014-05-21 | 日立オートモティブシステムズ株式会社 | 高圧燃料供給ポンプ |
-
2013
- 2013-08-23 DE DE102013216817.9A patent/DE102013216817A1/de not_active Withdrawn
-
2014
- 2014-08-11 KR KR1020167006726A patent/KR101857376B1/ko active IP Right Grant
- 2014-08-11 EP EP14749845.5A patent/EP2932086B1/de active Active
- 2014-08-11 JP JP2015558507A patent/JP6161731B2/ja active Active
- 2014-08-11 US US14/762,536 patent/US20160153366A1/en not_active Abandoned
- 2014-08-11 CN CN201480007079.9A patent/CN104956066B/zh active Active
- 2014-08-11 WO PCT/EP2014/067144 patent/WO2015024804A1/de active Application Filing
Non-Patent Citations (1)
Title |
---|
See references of WO2015024804A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE102013216817A1 (de) | 2015-02-26 |
KR20160042453A (ko) | 2016-04-19 |
US20160153366A1 (en) | 2016-06-02 |
CN104956066A (zh) | 2015-09-30 |
KR101857376B1 (ko) | 2018-05-11 |
CN104956066B (zh) | 2019-04-09 |
WO2015024804A1 (de) | 2015-02-26 |
JP6161731B2 (ja) | 2017-07-12 |
EP2932086B1 (de) | 2017-06-07 |
JP2016507699A (ja) | 2016-03-10 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1411238B1 (de) | Druckbegrenzungsventil für ein Kraftstoffeinspritzsystem | |
WO2015024804A1 (de) | Pumpenanordnung und system für ein kraftfahrzeug | |
DE102004013307B4 (de) | Kraftstoffhochdruckpumpe mit einem Druckbegrenzungsventil | |
DE10327411B4 (de) | Druckbegrenzungsventil sowie Kraftstoffsystem mit einem solchen Druckbegrenzungsventil | |
EP2938876B1 (de) | Druckbegrenzungsventil für ein kraftstoffeinspritzsystem und kraftstoffeinspritzsystem | |
DE102005033638A1 (de) | Kraftstoff-Fördereinrichtung, insbesondere für eine Brennkraftmaschine | |
WO2016075041A2 (de) | Niederdruckregelsystem einer kraftstofffördereinrichtung eines kraftstoffeinspritzsystems sowie ein absteuerventil dazu | |
DE102007010502A1 (de) | Kraftstoffhochdruckpumpe für eine Brennkraftmaschine mit Druckausgleichseinrichtung | |
EP1403509B1 (de) | Druckbegrenzungseinrichtung sowie Kraftstoffsystem mit einer solchen Druckbegrenzungseinrichtung | |
DE102009045113A1 (de) | Druckbegrenzungseinrichtung | |
WO2018054628A1 (de) | Kraftstoff-hochdruckpumpe | |
DE10118936A1 (de) | Druckbegrenzungseinrichtung sowie Kraftstoffsystem mit einer solchen Druckbegrenzungseinrichtung | |
DE102008036819B4 (de) | Überdrucksicherungsanordnung und Einspritzanlage für eine Brennkraftmaschine | |
WO2010060834A1 (de) | Hochdruckpumpe | |
WO2015022094A1 (de) | Hochdruckpumpe | |
DE102008058288A1 (de) | Druckbegrenzungsventil und Hochdruckpumpe mit einem Druckbegrenzungsventil | |
DE102010064189A1 (de) | Pumpe eines Kraftstoffeinspritzers | |
DE102011087664A1 (de) | Ventilanordnung | |
WO2004027250A1 (de) | Kraftstoffeinspritzanlage für brennkraftmaschinen | |
EP2399030B1 (de) | Einrichtung zur durchflussmengenbegrenzung an einer pumpe und pumpenanordnung mit solch einer einrichtung | |
DE102007016625A1 (de) | Ventil und Einspritzanlage für eine Brennkraftmaschine mit Ventil | |
WO2019166136A1 (de) | Druckbegrenzungsventil | |
DE102011089626A1 (de) | Druckbegrenzungsventil für eine Kraftstofffördereinrichtung sowie Kraftstofffördereinrichtung | |
DE102011089964A1 (de) | Drucksteuerventil für ein Kraftstoffeinspritzsystem sowie Kraftstoffeinspritzsystem | |
WO2022218850A1 (de) | Kraftstoff-hochdruckpumpe |
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: 20150622 |
|
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: 20170217 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
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 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP Ref country code: AT Ref legal event code: REF Ref document number: 899433 Country of ref document: AT Kind code of ref document: T Effective date: 20170615 |
|
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: 502014004127 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 4 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20170607 |
|
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: 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: 20170908 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: 20170607 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: 20170907 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: 20170607 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: 20170607 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: 20170607 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170607 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: 20170607 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: 20170607 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: 20170607 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: 20170907 |
|
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: 20170607 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: 20170607 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: 20170607 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: 20170607 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20170607 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: 20171007 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: 20170607 Ref country code: IT 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: 20170607 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502014004127 Country of ref document: DE |
|
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: 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: 20170607 |
|
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 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170831 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170831 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: 20170607 |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20170831 |
|
26N | No opposition filed |
Effective date: 20180308 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20170607 |
|
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: 20170811 |
|
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: 20170811 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 5 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170831 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20170607 |
|
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: 20140811 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20170607 |
|
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: 20170607 |
|
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: 20170607 |
|
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: 20170607 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R081 Ref document number: 502014004127 Country of ref document: DE Owner name: VITESCO TECHNOLOGIES GMBH, DE Free format text: FORMER OWNER: CONTINENTAL AUTOMOTIVE GMBH, 30165 HANNOVER, DE |
|
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: 20170607 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 899433 Country of ref document: AT Kind code of ref document: T Effective date: 20190811 |
|
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: 20190811 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R081 Ref document number: 502014004127 Country of ref document: DE Owner name: VITESCO TECHNOLOGIES GMBH, DE Free format text: FORMER OWNER: VITESCO TECHNOLOGIES GMBH, 30165 HANNOVER, DE |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: 732E Free format text: REGISTERED BETWEEN 20230427 AND 20230503 |
|
P01 | Opt-out of the competence of the unified patent court (upc) registered |
Effective date: 20230530 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20230822 Year of fee payment: 10 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20230824 Year of fee payment: 10 Ref country code: DE Payment date: 20230831 Year of fee payment: 10 |