EP2932086B1 - Ensemble pompe et système pour véhicule automobile - Google Patents

Ensemble pompe et système pour véhicule automobile Download PDF

Info

Publication number
EP2932086B1
EP2932086B1 EP14749845.5A EP14749845A EP2932086B1 EP 2932086 B1 EP2932086 B1 EP 2932086B1 EP 14749845 A EP14749845 A EP 14749845A EP 2932086 B1 EP2932086 B1 EP 2932086B1
Authority
EP
European Patent Office
Prior art keywords
pressure
limiting valve
valve
pump
relief valve
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.)
Active
Application number
EP14749845.5A
Other languages
German (de)
English (en)
Other versions
EP2932086A1 (fr
Inventor
Ulf STEINERT
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Continental Automotive GmbH
Original Assignee
Continental Automotive GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Continental Automotive GmbH filed Critical Continental Automotive GmbH
Publication of EP2932086A1 publication Critical patent/EP2932086A1/fr
Application granted granted Critical
Publication of EP2932086B1 publication Critical patent/EP2932086B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/02—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 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 pressure relief valve is conventionally coupled to the high-pressure piston chamber of the pump, the valve can open only during the suction phase of the pump. During the pressure phase of the pump, the valve is hydraulically locked and can not open.
  • DE 10 2010 064 192 A1 describes a pressure-switching valve for a fuel injection system of an internal combustion engine, with a cylinder in which a closure body for selectively closing an inlet is movable, wherein in the pressure-switching valve, the closure body is provided with a first effective area, the hydraulic pressure to open the inlet acts, and the closure body has a second active surface, which is designed larger than the first active surface.
  • 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 conveying a fluid.
  • 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 limiting valve ensures, in particular, that the maximum permissible pressure at the fluid outlet of the high-pressure pump is not exceeded.
  • the value of the opening pressure of the first pressure limiting valve is in particular greater than the system pressures occurring in normal operation in the pressure phase of the high pressure pump.
  • the first pressure relief 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 pressure-limiting valve permits opening in each suction phase of the high-pressure pump in order to damp occurring pressure pulsations. This makes it possible to protect the first pressure relief valve from wear, since the first pressure relief valve remains closed during normal operation and opens only in the event of a fault.
  • 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, to open the first pressure relief valve during the pressure phase of the high-pressure pump. 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 can be discharged. Thus, it is ensured by the first pressure relief valve during the entire working cycle of the high pressure pump, that the maximum allowable pressure in the fluid flow is not exceeded. In the event of a fault, it is possible that the entire volume flow conveyed by the high-pressure pump is discharged again into the low-pressure region at the fluid inlet without appreciable increase in pressure. An impermissible increase in pressure during the printing phase is avoided.
  • the second pressure relief valve is hydraulically coupled to the pressure chamber on the output side. This is a hydraulic closure of the second pressure relief valve during the pressure phase of the high-pressure pump possible. Thus, a good efficiency of the pump is achieved because the entire volume of a pumping cycle is promoted to the fluid drain. By the first pressure relief valve, the pump assembly is always protected against unacceptably high pressures.
  • the second pressure limiting valve is coupled on the input side with the fluid outlet.
  • a hydraulic communication between the fluid drain and the fluid inlet is possible with the second pressure relief valve open.
  • the second pressure relief valve opens during each pressure phase.
  • pressure pulsations on the fluid drain are minimized.
  • the dead volume within the high-pressure pump is reduced, whereby an increase in efficiency is effected.
  • 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 with the second pressure relief valve is possible. 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 relief valve is designed as a passive pressure control valve with fixed 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-limiting valve is predetermined in particular as a function of the high-pressure manifold.
  • the value of the opening pressure is in particular predetermined so that a maximum predetermined pressure for the high-pressure manifold is not exceeded.
  • the value of the opening pressure of the second pressure-limiting valve is predetermined in particular as a function of the lowest opening pressure of the injector. This ensures reliable operation of the injector.
  • FIG. 1 shows a pump assembly 100.
  • the pump assembly 100 is in particular 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 fluid outlet 103 is in particular coupled to a high-pressure manifold 112.
  • An injector 107 or several injectors 107 are coupled to the high-pressure manifold.
  • the injectors are configured to inject motor vehicles into an associated combustion chamber of an internal combustion engine during operation.
  • the high pressure pump 101 the fluid is conveyed from the fluid tank 113 and conveyed under pressure of a high pressure manifold 112.
  • On the low pressure side 114 prevail in operation, for example, pressures of less than 5 bar.
  • the high-pressure pump 101 is in particular a piston pump.
  • a piston 122 is arranged in the pressure chamber 104. If the piston 121 moves along its longitudinal axis so that the volume of the pressure chamber 104 increases, fluid is sucked through the fluid inlet 102 into the pressure chamber 104. This is the so-called suction phase of the high-pressure pump 101. Subsequently, the piston 122 is moved in the reverse direction and the fluid is expelled from the pressure chamber 104 into the fluid outlet 103. This is the so-called pressure phase of the high-pressure pump 101.
  • the pump arrangement 100 has a first pressure limiting valve 105.
  • An input side 108 of the pressure relief valve 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 fluid flow through the pressure relief valve 105 at pressures 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 pressure-limiting valve 105 is predetermined so that a predetermined maximum pressure in the fluid outlet 103 and in particular in the high-pressure manifold 112 is not exceeded.
  • the first Pressure limiting valve 105 is closed during normal operation of the pump assembly 100. 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.
  • the pressure on the high-pressure side 115 is kept within predetermined upper limits.
  • 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 relief 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 pressure relief valve 106 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.
  • the second pressure relief valve 106 is hydraulically coupled with its input side 109 to the fluid drain 103.
  • An output side 111 of the second pressure relief valve 106 is hydraulically coupled to the pressure chamber 104.
  • the second pressure relief valve 106 is according to the embodiments, as in FIG. 1 shown during the pressure phase of the high-pressure pump 101 hydraulically locked.
  • 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 Maschinenschensdrucks.
  • the value of the opening pressure of the second pressure relief valve 106 is below the highest allowable pressure of the injector 107.
  • the function of the injector 107 is ensured, so a reliable opening and injecting fluid into the combustion chamber.
  • the second pressure limiting valve 106 can open during the suction phase of the high-pressure pump 101, pressure pulsations in the fluid outlet 103 and in the high-pressure manifold 112 are reduced. Characterized in that the second pressure relief valve 106 can open only in the suction phase of the high-pressure pump 101, the efficiency of the pump assembly 100 is good.
  • the use of a passive pressure control valve with a predetermined value of the opening pressure also allows a calibration of a pressure sensor 123.
  • the pressure sensor 123 is set up, to determine the fluid pressure in the high pressure manifold 112.
  • the predetermined value of the opening pressure of the second pressure relief valve 106 is not changed during operation in particular. This makes it possible to calibrate the pressure sensor 123 against the fixed referenced value of the opening pressure of the second pressure relief valve 106.
  • This is not possible with a conventionally used actively controlled pressure control valve, since the opening pressure in the case of an active valve can be adjusted to different values of the opening pressure via the applied control voltage 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 pressure limiting valve 106 are in particular predetermined so that a maximum permissible surface pressure is not exceeded despite high fluid pressures.
  • the second pressure relief valve 106 is designed in particular durable.
  • the value of the opening pressure of the first pressure limiting valve 105 is so high that pressure pulsations do not lead to opening of the first pressure limiting valve 105 during operation of the pump arrangement 100.
  • the first pressure limiting valve 105 is connected with its output side 110 to the low pressure region 114.
  • a pressure reduction is independent of the suction phase and the pressure phase of the high-pressure pump 101 possible.
  • 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 pressure limiting valve 105 is set above the system pressures occurring in normal operation in the pressure phase.
  • 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.
  • the first pressure relief valve 105 opens only in the event of a fault. Since the first pressure relief valve 105 does not open in normal operation, the wear of the first pressure relief valve 105 is reduced.
  • the first pressure relief valve 105 and the second pressure relief valve 106 are hydraulically connected in parallel on the input side.
  • FIG. 2 shows a non-inventive pump assembly 100.
  • the pump assembly 100 of FIG. 2 corresponds substantially to the embodiments of the pump assembly 100 as in connection with FIG. 1 explained.
  • 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 relief valve 106 is not hydraulically closed during the pressure phase of the high-pressure pump 101. Thus, it is possible that the second pressure relief valve 106 opens during the pressure 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 an increase in efficiency of the pump assembly 100.
  • FIG. 3 shows a non-inventive pump assembly 100.
  • the pump assembly 100 according to FIG. 3 corresponds substantially to the embodiments as in connection with the Figures 1 and 2 explained.
  • the input side 109 of the second pressure relief valve 106 is hydraulically connected to the pressure chamber 104.
  • the output side 111 of the second pressure relief valve 106 is hydraulically connected to the fluid inlet 102 and the low pressure side 114, respectively.
  • 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 relief valve 105 and the second pressure relief valve 106, which are hydraulically connected in parallel.
  • the value of the opening pressure of the first pressure-limiting valve 105 is set greater than the value of the opening pressure of the second pressure-limiting valve 106.
  • 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 and the value of the maximum volume flow of the first pressure-limiting valve 105 are predetermined so that a maximum predetermined pressure in the high pressure region 115 is never exceeded when functioning first pressure relief valve 105.
  • the value of the opening pressure and the value of the maximum volume flow of the second pressure relief valve 106 are predetermined so that a safe opening of the injectors 107 is ensured as well as pressure pulsations are damped.
  • FIG. 5 shows a schematic representation of the second pressure limiting valve 106 according to an embodiment.
  • 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.
  • 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.
  • On the input side 109 for example, a tapered cross-section 121 is provided, which serves to limit the flow.
  • the value of the opening pressure of the second pressure relief valve 106 is set by the bias of the spring 116.
  • the bias of the spring 116 is adjusted.
  • the bias voltage 116 reaches a predetermined value
  • the position of the holding member 119 relative to the housing 120 is fixed.
  • the value of the opening pressure of the second pressure limiting valve 106 can thus be simply predetermined. 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 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 pressure relief valve 106 is integrated according to embodiments directly into a housing of the pump 101.
  • 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 to allow a low-emission operation of the internal combustion engine at a pressure on the high pressure side 115 of up to 350 bar. At the system pressure up to 350 bar, the tightness of the connection between the high-pressure manifold 112 and the injector 107 is ensured via an O-ring.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (8)

  1. Ensemble de pompe pour un véhicule automobile, présentant:
    - une pompe haute pression (101) pour refouler un fluide, comprenant une alimentation en fluide (102) et une évacuation de fluide (103) ainsi qu'un espace de pression (104) qui est disposé hydrauliquement entre l'alimentation en fluide (102) et l'évacuation de fluide (103),
    - une première soupape de limitation de pression (105), qui est accouplée du côté de l'entrée à l'évacuation de fluide (103),
    - une deuxième soupape de limitation de pression (106),
    - les deux soupapes de limitation de pression (105, 106) étant branchées en parallèle hydrauliquement,
    - les deux soupapes de limitation de pression (105, 106) présentant chacune une pression d'ouverture,
    - la valeur de la pression d'ouverture de la première soupape de limitation de pression (105) étant supérieure à la valeur de la pression d'ouverture de la deuxième soupape de limitation de pression (106), et
    - la valeur de la pression d'ouverture de la deuxième soupape de limitation de pression (106) étant prédéfinie en fonction d'un injecteur (107) pouvant être accouplé hydrauliquement à l'agencement de pompe (100),
    caractérisé en ce que la deuxième soupape de limitation de pression (106) est accouplée hydrauliquement du côté de la sortie à l'espace de pression (104).
  2. Agencement de pompe selon la revendication 1, dans lequel la première soupape de limitation de pression (105) est accouplée hydrauliquement du côté de la sortie à l'alimentation en fluide (102).
  3. Agencement de pompe selon l'une quelconque des revendications 1 ou 2, dans lequel la deuxième soupape de limitation de pression (106) est accouplée du côté de l'entrée à l'évacuation de fluide (103).
  4. Agencement de pompe selon l'une quelconque des revendications 1 à 3, dans lequel la deuxième soupape de limitation de pression (106) est accouplée du côté de l'entrée à l'espace de pression (104).
  5. Agencement de pompe selon l'une quelconque des revendications 1 à 4, dans lequel la deuxième soupape de limitation de pression (106) est réalisée sous forme de soupape de régulation de pression passive avec une pression d'ouverture ajustée de manière fixe.
  6. Agencement de pompe selon l'une quelconque des revendications 1 à 5, dans lequel la valeur de la pression d'ouverture de la première soupape de limitation de pression (105) est prédéfinie en fonction d'une conduite de collecte haute pression (112) pouvant être accouplée hydrauliquement entre l'évacuation de fluide (103) et l'injecteur (107).
  7. Agencement de pompe selon l'une quelconque des revendications 1 à 6, dans lequel la valeur de la pression d'ouverture de la deuxième soupape de limitation de pression (106) est prédéfinie en fonction de la pression d'ouverture de l'injecteur (107).
  8. Système comprenant :
    - un agencement de pompe (100) selon l'une quelconque des revendications 1 à 7,
    - une conduite de collecte haute pression (112) qui est accouplée hydrauliquement à l'évacuation de fluide,
    - l'injecteur (107) pour injecter le fluide dans une chambre de combustion d'un moteur à combustion interne.
EP14749845.5A 2013-08-23 2014-08-11 Ensemble pompe et système pour véhicule automobile Active EP2932086B1 (fr)

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 (fr) 2013-08-23 2014-08-11 Ensemble pompe et système pour véhicule automobile

Publications (2)

Publication Number Publication Date
EP2932086A1 EP2932086A1 (fr) 2015-10-21
EP2932086B1 true EP2932086B1 (fr) 2017-06-07

Family

ID=51300765

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14749845.5A Active EP2932086B1 (fr) 2013-08-23 2014-08-11 Ensemble pompe et système pour véhicule automobile

Country Status (7)

Country Link
US (1) US20160153366A1 (fr)
EP (1) EP2932086B1 (fr)
JP (1) JP6161731B2 (fr)
KR (1) KR101857376B1 (fr)
CN (1) CN104956066B (fr)
DE (1) DE102013216817A1 (fr)
WO (1) WO2015024804A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
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
FI3819493T3 (fi) * 2019-11-08 2024-03-28 Chongqing hongjiang machinery co ltd Korkeapaineinen, useita turvallisuustoimintoja sisältävä yhteispaineruiskutusjärjestelmä hidaskäyntiseen moottoriin

Family Cites Families (18)

* Cited by examiner, † Cited by third party
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 (fr) * 2002-10-15 2006-01-11 Robert Bosch Gmbh Soupape de limitation de pression pour un système d'injection de carburant
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
DE102010064171A1 (de) * 2010-12-27 2012-06-28 Robert Bosch Gmbh Druckregelanordnung eines Kraftstoffversorgungssystems
DE102010064192A1 (de) * 2010-12-27 2012-06-28 Robert Bosch Gmbh Druck-Schaltventil für ein Kraftstoffeinspritzsystem einer Brennkraftmaschine
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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
KR20160042453A (ko) 2016-04-19
WO2015024804A1 (fr) 2015-02-26
JP6161731B2 (ja) 2017-07-12
CN104956066B (zh) 2019-04-09
EP2932086A1 (fr) 2015-10-21
DE102013216817A1 (de) 2015-02-26
US20160153366A1 (en) 2016-06-02
CN104956066A (zh) 2015-09-30
KR101857376B1 (ko) 2018-05-11
JP2016507699A (ja) 2016-03-10

Similar Documents

Publication Publication Date Title
EP2932086B1 (fr) Ensemble pompe et système pour véhicule automobile
EP1411238B1 (fr) Soupape de limitation de pression pour un système d'injection de carburant
DE10327411B4 (de) Druckbegrenzungsventil sowie Kraftstoffsystem mit einem solchen Druckbegrenzungsventil
EP2938876B1 (fr) Soupape de limitation de pression pour système d'injection de carburant et système d'injection de carburant
WO2016075041A2 (fr) Système de régulation basse pression d'un dispositif de refoulement de carburant d'un système d'injection de carburant ainsi que clapet de refoulement associé
DE102005033638A1 (de) Kraftstoff-Fördereinrichtung, insbesondere für eine Brennkraftmaschine
DE102007010502A1 (de) Kraftstoffhochdruckpumpe für eine Brennkraftmaschine mit Druckausgleichseinrichtung
WO2018054628A1 (fr) Pompe à carburant à haute pression
EP1403509B1 (fr) Dispositif de limitation de pression et système de combustible avec tel dispositif de limitation de pression
DE102009045113A1 (de) Druckbegrenzungseinrichtung
EP2694796B1 (fr) Soupape de vidange pour systèmes d'injection d'huile lourde à rampe commune
EP3039280A1 (fr) Soupape de décharge pour système d'injection de carburant ainsi que système d'injection de carburant
EP3084200B1 (fr) Dispositif d'alimentation en carburant d'un système d'injection de carburant d'un moteur à combustion interne, ainsi que soupape de décharge associée
DE102008036819B4 (de) Überdrucksicherungsanordnung und Einspritzanlage für eine Brennkraftmaschine
WO2010060834A1 (fr) Pompe haute pression
DE102011087664B4 (de) Ventilanordnung
DE102008058288A1 (de) Druckbegrenzungsventil und Hochdruckpumpe mit einem Druckbegrenzungsventil
DE102020210846A1 (de) Kraftstoffhochdruckpumpe
WO2016045820A1 (fr) Injecteur de carburant
DE102007016625A1 (de) Ventil und Einspritzanlage für eine Brennkraftmaschine mit Ventil
DE102011089626A1 (de) Druckbegrenzungsventil für eine Kraftstofffördereinrichtung sowie Kraftstofffördereinrichtung
EP1947324A2 (fr) Injecteur de carburant doté d'un amplificateur de pression intégré
DE10355124B4 (de) Druckbegrenzungsventil für Kraftstoff-Einspritzeinrichtungen
DE102011089964A1 (de) Drucksteuerventil für ein Kraftstoffeinspritzsystem sowie Kraftstoffeinspritzsystem
DE102008045022A1 (de) Dichtungsanordnung für ein Gehäuse, und Pumpe

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: DE

Payment date: 20240831

Year of fee payment: 11

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

Ref country code: GB

Payment date: 20240826

Year of fee payment: 11

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

Ref country code: FR

Payment date: 20240829

Year of fee payment: 11