EP2932086B1 - Pump arrangement and system for a motor vehicle - Google Patents

Pump arrangement and system for a motor vehicle Download PDF

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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
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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
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German (de)
French (fr)
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EP2932086A1 (en
Inventor
Ulf STEINERT
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Continental Automotive GmbH
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Continental Automotive GmbH
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Publication date
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Publication of EP2932086A1 publication Critical patent/EP2932086A1/en
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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.

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  • 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)

Description

Die Erfindung betrifft eine Pumpenanordnung für ein Kraftfahrzeug. Weiterhin betrifft die Erfindung ein System mit einer Pumpenanordnung für ein Kraftfahrzeug, insbesondere ein Kraftstoffeinspritzsystem.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.

Pumpen zur Fluidförderung, insbesondere eine Pumpe zur Kraftstoffförderung für ein Einspritzsystem eines Kraftfahrzeugs, weisen herkömmlich ein Druckbegrenzungsventil auf. Dieses Ventil ist an der Hochdruckseite der Pumpe angeordnet. Das Ventil ist so ausgelegt, dass im Fehlerfall der maximal von der Hochdruckpumpe gefördertem Volumenstrom wieder zurück in den Hochdruckkolbenraum der Pumpe gelangen kann. Dadurch wird das Hochdrucksystem mit der Pumpe vor unzulässig hohen Drücken geschützt. Unter normalen Betriebsbedingungen ist das Ventil geschlossen. Dadurch, dass das Druckbegrenzungsventil herkömmlich mit dem Hochdruckkolbenraum der Pumpe gekoppelt ist, kann das Ventil nur während der Saugphase der Pumpe öffnen. Während der Druckphase der Pumpe ist das Ventil hydraulisch verriegelt und kann nicht öffnen.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. Characterized in that 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 beschreibt ein Druck-Schaltventil für ein Kraftstoffeinspritzsystem einer Brennkraftmaschine, mit einem Zylinder, in dem ein Verschlusskörper zum wahlweisen Verschließen eines Einlasses beweglich ist, wobei in dem Druck-Schaltventil der Verschlusskörper mit einer ersten Wirkfläche versehen ist, auf die hydraulischer Druck zum Öffnen des Einlasses wirkt, und der Verschlusskörper weist eine zweite Wirkfläche auf, die größer als die erste Wirkfläche gestaltet ist. 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.

Es ist wünschenswert, eine Pumpenanordnung für ein Kraftfahrzeug anzugeben, die einen verlässlichen Betrieb ermöglicht. Es ist weiterhin wünschenswert, ein System in einer Pumpenanordnung anzugeben, das einen verlässlichen Betrieb ermöglicht.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.

Die Erfindung betrifft eine Pumpenanordnung für ein Kraftfahrzeug sowie ein System, das eine solche Pumpenanordnung umfasst.The invention relates to a pump assembly for a motor vehicle and a system comprising such a pump assembly.

Gemäß zumindest einer Ausführungsform der Erfindung weist die Pumpenanordnung eine Hochdruckpumpe zur Förderung eines Fluids auf. Die Hochdruckpumpe weist einem Fluidzulauf und einem Fluidablauf sowie einem Druckraum auf, der hydraulisch zwischen dem Fluidzulauf und dem Fluidablauf angeordnet ist. Die Pumpenanordnung weist ein erstes Druckbegrenzungsventil auf, das eingangsseitig mit dem Fluidablauf gekoppelt ist. Die Pumpenanordnung weist ein zweites Druckbegrenzungsventil auf. Die beiden Druckbegrenzungsventile sind hydraulisch parallel geschaltet. Die beiden Druckbegrenzungsventile weisen jeweils einen Öffnungsdruck auf. Der Wert des Öffnungsdrucks des ersten Druckbegrenzungsventils ist größer als der Wert des Öffnungsdrucks des zweiten Druckbegrenzungsventils. Die Pumpenanordnung ist hydraulisch mit einem Injektor koppelbar. Der Wert des Öffnungsdrucks des zweiten Druckbegrenzungsventils ist in Abhängigkeit von dem Injektor vorgegeben.In accordance with at least one embodiment of the invention, 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.

Durch das erste Druckbegrenzungsventil wird insbesondere sichergestellt, dass der maximal zulässige Druck am Fluidablauf der Hochdruckpumpe nicht überschritten wird. Um ein unnötiges Öffnen des ersten Druckbegrenzungsventils zu vermeiden, ist der Wert des Öffnungsdrucks des ersten Druckbegrenzungsventils insbesondere größer als die im normalen Betrieb auftretenden Systemdrücke in der Druckphase der Hochdruckpumpe. Somit öffnet das erste Druckbegrenzungsventil im Normalbetrieb nicht. Im Fehlerfall schützt das erste Druckbegrenzungsventil vor zu hohen Drücken.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. To avoid unnecessary opening of the first pressure limiting valve, 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. Thus, 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.

Durch das zweite Druckbegrenzungsventil wird ein verlässliches Öffnen der mit der Pumpenanordnung koppelbaren Injektoren gewährleistet. Der Wert des Öffnungsdrucks des zweiten Druckbegrenzungsventils wird so vorgegeben, dass der Wert des Öffnungsdrucks unterhalb des höchsten zulässigen Drucks für den Injektor liegt. Damit wird die Funktion der Injektoren sichergestellt. Unter dem höchsten zulässigen Druck für den Injektor ist dabei der Fluiddruck zu verstehen, bei dem der Injektor gerade noch zuverlässig öffnen kann.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.

Insbesondere ist es möglich, dass das zweite Druckbegrenzungsventil ein Öffnen in jeder Saugphase der Hochdruckpumpe zulässt, um auftretende Druckpulsationen zu dämpfen. Dadurch ist es möglich, das erste Druckbegrenzungsventil vor Verschleiß zu schützen, da das erste Druckbegrenzungsventil im Normalbetrieb geschlossen bleibt und nur im Fehlerfall öffnet.In particular, it is possible for the second pressure-limiting valve to permit 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.

Gemäß weiteren Ausführungsformen ist das erste Druckbegrenzungsventil ausgangsseitig hydraulisch mit dem Fluidzulauf gekoppelt. Dadurch ist es möglich, im Fehlerfall auch während der Druckphase der Hochdruckpumpe das erste Druckbegrenzungsventil zu öffnen. Ein hydraulisch verschlossenes Druckbegrenzungsventil ist somit vermeidbar. Das erste Druckbegrenzungsventil wird so ausgelegt, dass der maximale Volumenstrom der Hochdruckpumpe durch das erste Druckbegrenzungsventil abführbar ist. Somit wird durch das erste Druckbegrenzungsventil während des gesamten Arbeitszyklus der Hochdruckpumpe gewährleistet, dass der maximal zulässige Druck im Fluidablauf nicht überschritten wird. Im Fehlerfall ist es möglich, dass der gesamte von der Hochdruckpumpe geförderte maximale Volumenstrom ohne nennenswerten Druckanstieg wieder in den Niederdruckbereich am Fluidzulauf abgeführt wird. Ein unzulässiger Druckanstieg während der Druckphase wird vermieden.According to further embodiments, 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.

Das zweite Druckbegrenzungsventil ist ausgangsseitig hydraulisch mit dem Druckraum gekoppelt. Dadurch ist ein hydraulischer Verschluss des zweiten Druckbegrenzungsventils während der Druckphase der Hochdruckpumpe möglich. Somit wird ein guter Wirkungsgrad der Pumpe erzielt, da das gesamte Volumen eines Pumpzyklus zum Fluidablauf gefördert wird. Durch das erste Druckbegrenzungsventil ist die Pumpenanordnung stets vor unzulässig hohen Drücken geschützt.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.

Gemäß Ausführungsformen ist das zweite Druckbegrenzungsventil eingangsseitig mit dem Fluidablauf gekoppelt. Somit ist eine hydraulische Kommunikation zwischen dem Fluidablauf und dem Fluidzulauf bei geöffnetem zweiten Druckbegrenzungsventil möglich. Somit ist es möglich, dass das zweite Druckbegrenzungsventil während jeder Druckphase öffnet. Somit werden Druckpulsationen am Fluidablauf minimiert. Das Totvolumen innerhalb der Hochdruckpumpe wird verkleinert, wodurch eine Wirkungsgradsteigerung bewirkt wird.According to embodiments, the second pressure limiting valve is coupled on the input side with the fluid outlet. Thus, a hydraulic communication between the fluid drain and the fluid inlet is possible with the second pressure relief valve open. Thus, it is possible that the second pressure relief valve opens during each pressure phase. Thus, 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.

Gemäß weiteren Ausführungsformen ist das zweite Druckbegrenzungsventil eingangsseitig mit dem Druckraum gekoppelt. Somit ist eine hydraulische Kommunikation zwischen dem Druckraum und dem Fluidzulauf bei geöffnetem zweiten Druckbegrenzungsventil möglich. Dadurch ist es möglich, Druckpulsationen im Druckraum und am Fluidablauf zu minimieren. Das zweite Druckbegrenzungsventil kann in jeder Druckphase der Hochdruckpumpe öffnen.According to further embodiments, the second pressure relief valve is coupled on the input side to the pressure chamber. Thus, 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.

Gemäß weiteren Ausführungsformen ist das zweite Druckbegrenzungsventil als passives Druckregelventil mit fest eingestelltem Öffnungsdruck ausgebildet. Beispielsweise ist es mittels des zweiten Druckbegrenzungsventils möglich, eine Kalibrierung eines Drucksensors am Fluidablauf durchzuführen. Dazu wird beispielsweise der Systemdruck auf den Wert des Öffnungsdrucks des zweiten Druckbegrenzungsventils angehoben. Dadurch, dass der Öffnungsdruck fest eingestellt ist, kann der Wert des Öffnungsdrucks als Referenz verwendet werden. Gemäß weiteren Ausführungsformen ist der Fluidablauf mit einer Hochdrucksammelleitung koppelbar. Mit der Hochdrucksammelleitung ist der Injektor koppelbar. Der Wert des Öffnungsdrucks des ersten Druckbegrenzungsventils ist insbesondere in Abhängigkeit von der Hochdrucksammelleitung vorgegeben. Der Wert des Öffnungsdrucks ist insbesondere so vorgegeben, dass ein maximal vorgegebener Druck für die Hochdrucksammelleitung nicht überschritten wird.According to further embodiments, the second pressure relief valve is designed as a passive pressure control valve with fixed opening pressure. For example, it is possible by means of the second pressure limiting valve to carry out a calibration of a pressure sensor on the fluid outlet. For example, 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. According to further embodiments, 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.

Der Wert des Öffnungsdrucks des zweiten Druckbegrenzungsventils ist insbesondere in Abhängigkeit von dem niedrigsten Öffnungsdruck des Injektors vorgegeben. Dadurch wird ein zuverlässiger Betrieb des Injektors gewährleistet.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.

Weitere Vorteile, Merkmale und Weiterbildungen ergeben sich aus den nachfolgenden in Verbindung mit den Figuren erläuterten Beispielen. Gleiche, gleichartige und gleich wirkende Elemente können dabei mit den gleichen Bezugszeichen versehen sein.Further advantages, features and developments emerge from the following examples explained in conjunction with the figures. Identical, similar and equally acting elements can be provided with the same reference numerals.

Es zeigen:

  • Figur 1 eine schematische Darstellung eines Kraftstoffeinspritzsystems gemäß Ausführungsformen,
  • Figur 2 eine schematische Darstellung eines nicht erfindungsgemäßen Kraftstoffeinspritzsystems gemäß Ausführungsformen,
  • Figur 3 eine schematische Darstellung eines nicht erfindungsgemäßen Kraftstoffeinspritzsystems gemäß Ausführungsformen,
  • Figur 4 eine schematische Detailansicht einer Pumpenanordnung gemäß Ausführungsformen, und
  • Figur 5 eine schematische Darstellung eines Druckbegrenzungsventils gemäß Ausführungsformen.
Show it:
  • FIG. 1 a schematic representation of a fuel injection system according to embodiments,
  • FIG. 2 a schematic representation of a non-inventive fuel injection system according to embodiments,
  • FIG. 3 a schematic representation of a non-inventive fuel injection system according to embodiments,
  • FIG. 4 a schematic detail view of a pump assembly according to embodiments, and
  • FIG. 5 a schematic representation of a pressure relief valve according to embodiments.

Figur 1 zeigt eine Pumpenanordnung 100. Die Pumpenanordnung 100 ist insbesondere Teil eines Kraftstoffeinspritzsystems eines Kraftfahrzeugs. Das Kraftstoffeinspritzsystem ist insbesondere ein so genanntes Common-Rail-Einspritzsystem. Die Pumpenanordnung 100 weist eine Hochdruckpumpe 101 mit einem Fluidzulauf 102 und einen Fluidablauf 103 auf. Hydraulisch zwischen dem Fluidzulauf 102 und dem Fluidablauf 103 ist ein Druckraum 104 vorgesehen. 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.

Der Fluidzulauf 102 ist auf einer Niederdruckseite 114 angeordnet. Der Fluidzulauf 102 dient insbesondere zur Kopplung des Druckraums 104 mit einem Fluidtank 113. Der Fluidablauf 103 ist auf einer Hochdruckseite 115 vorgesehen. Der Fluidablauf 103 ist insbesondere mit einer Hochdrucksammelleitung 112 gekoppelt. Mit der Hochdrucksammelleitung ist ein Injektor 107 beziehungsweise sind mehrere Injektoren 107 gekoppelt. Die Injektoren sind dazu eingerichtet, im Betrieb Kraftfahrzeug in jeweils einen zugeordneten Brennraum einer Brennkraftmaschine einzuspritzen. Mittels der Hochdruckpumpe 101 wird das Fluid aus dem Fluidtank 113 gefördert und unter Beaufschlagung eines Drucks in die Hochdrucksammelleitung 112 gefördert. Auf der Niederdruckseite 114 herrschen im Betrieb beispielsweise Drücke von unter 5 bar. Auf der Hochdruckseite 115 und insbesondere in der Kraftstoffsammelleitung 112 herrschen insbesondere Drücke von über 300 bar, beispielsweise 350 bar oder mehr.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. By means of 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. On the high pressure side 115 and in particular prevail in the fuel rail 112 in particular pressures of over 300 bar, for example 350 bar or more.

Die Hochdruckpumpe 101 ist insbesondere eine Kolbenpumpe. Im Druckraum 104 ist ein Kolben 122 angeordnet. Bewegt sich der Kolben 121 entlang seiner Längsachse so, dass sich das Volumen des Druckraums 104 vergrößert, wird Fluid durch den Fluidzulauf 102 in den Druckraum 104 eingesaugt. Dies ist die sogenannte Saugphase der Hochdruckpumpe 101. Nachfolgend wird der Kolben 122 in umgekehrter Richtung bewegt und das Fluid aus dem Druckraum 104 in den Fluidablauf 103 ausgestoßen. Dies ist die sogenannte Druckphase der Hochdruckpumpe 101.The high-pressure pump 101 is in particular a piston pump. In the pressure chamber 104, a piston 122 is arranged. 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.

Die Pumpenanordnung 100 weist ein erstes Druckbegrenzungsventil 105 auf. Eine Eingangsseite 108 des Druckbegrenzungsventils 105 ist hydraulisch mit dem Fluidablauf 103 verbunden. Eine Ausgangsseite 110 des ersten Druckbegrenzungsventils 105 ist hydraulisch mit dem Fluidzulauf 102 verbunden. Die Eingangsseite 108 des ersten Druckbegrenzungsventils 105 ist mit der Hochdruckseite 115 hydraulisch gekoppelt. Die Ausgangsseite 110 des ersten Druckbegrenzungsventils 105 ist mit der Niederdruckseite 114 hydraulisch gekoppelt.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.

Das erste Druckbegrenzungsventil 105 weist einen vorgegebenen Öffnungsdruck auf. Das Druckbegrenzungsventil 105 sperrt einen Fluidfluss durch das Druckbegrenzungsventil 105 bei Drücken unterhalb des vorgegebenen Öffnungsdruck. Bei Drücken ab dem vorgegebenen Öffnungsdruck gibt das Druckbegrenzungsventil 105 einen Fluidfluss durch das Druckbegrenzungsventil 105 frei. Der Wert des Öffnungsdrucks des ersten Druckbegrenzungsventils 105 ist so vorgegeben, dass ein vorgegebener maximaler Druck im Fluidablauf 103 und insbesondere in der Hochdrucksammelleitung 112 nicht überschritten wird. Das erste Druckbegrenzungsventil 105 ist im Normalbetrieb der Pumpenanordnung 100 geschlossen. Wird der vorgegebene Wert des Öffnungsdrucks an der Eingangsseite 108 erreicht und/oder überschritten, öffnet das erste Druckbegrenzungsventil 105 und gibt einen Fluidfluss von der Eingangsseite 108 zu der Ausgangsseite 110 frei. Somit wird der Druck auf der Hochdruckseite 115 innerhalb von vorgegebenen Höchstgrenzen gehalten. Dadurch, dass das erste Druckbegrenzungsventil 105 mit dem Fluidzulauf 102 hydraulisch verbunden ist, ist es möglich, dass das erste Druckbegrenzungsventil 105 sowohl während der Saugphase der Hochdruckpumpe 101 als auch während der Druckphase der Hochdruckpumpe 101 öffnet. Das erste Druckbegrenzungsventil 105 ist nicht hydraulisch verriegelt.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. Thus, the pressure on the high-pressure side 115 is kept within predetermined upper 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.

Die Pumpenanordnung 100 weist ein zweites Druckbegrenzungsventil 106 auf. Das zweite Druckbegrenzungsventil 106 ist insbesondere ein passives Druckregelventil. Das zweite Druckbegrenzungsventil 106 weist einen Öffnungsdruck auf, dessen Wert vorgegeben ist. Das zweite Druckbegrenzungsventil 106 weist einen vorgegebenen Öffnungsdruck auf. Das Druckbegrenzungsventil 106 sperrt einen Fluidfluss durch das Druckbegrenzungsventil 106 bei Drücken unterhalb des vorgegebenen Öffnungsdruck. Bei Drücken ab dem vorgegebenen Öffnungsdruck gibt das Druckbegrenzungsventil 106 einen Fluidfluss durch das Druckbegrenzungsventil 106 frei.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.

Der Wert des Öffnungsdrucks des zweiten Druckbegrenzungsventils ist kleiner als der Wert des Öffnungsdrucks des ersten Druckbegrenzungsventils. In den Ausführungsbeispielen wie in Figur 1 dargestellt, ist das zweite Druckbegrenzungsventil 106 mit seiner Eingangsseite 109 mit dem Fluidablauf 103 hydraulisch gekoppelt. Eine Ausgangsseite 111 des zweiten Druckbegrenzungsventils 106 ist mit dem Druckraum 104 hydraulisch gekoppelt.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. In the embodiments as in FIG. 1 illustrated, 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.

Bei geöffnetem zweiten Druckbegrenzungsventil 106 ist somit ein Fluidfluss von dem Fluidablauf 103 in den Druckraum 104 möglich. Das zweite Druckbegrenzungsventil 106 ist gemäß den Ausführungsbeispielen, wie in Figur 1 dargestellt, während der Druckphase der Hochdruckpumpe 101 hydraulisch verriegelt. Das zweite Druckbegrenzungsventil 106 kann sich nur während der Saugphase der Hochdruckpumpe 101 öffnen und ist während einer Druckphase der Hochdruckpumpe 101 stets geschlossen. Der Wert des Öffnungsdrucks des zweiten Druckbegrenzungsventils ist insbesondere in Abhängigkeit des Injektors 107 vorgegeben. Der Wert des Öffnungsdrucks des zweiten Druckbegrenzungsventils 106 ist in Abhängigkeit des höchsten zulässigen Injektoröffnungsdrucks vorgegeben. Dadurch wird ein verlässlicher Betrieb der Injektoren 107 ermöglicht. Insbesondere ist der Wert des Öffnungsdrucks des zweiten Druckbegrenzungsventils 106 unterhalb des höchsten zulässigen Drucks des Injektors 107. Somit wird die Funktion des Injektors 107 sichergestellt, also ein zuverlässiges Öffnen und Einspritzen von Fluid in den Brennraum. Dadurch, dass das zweite Druckbegrenzungsventil 106 während der Saugphase der Hochdruckpumpe 101 öffnen kann, werden Druckpulsationen im Fluidablauf 103 und in der Hochdrucksammelleitung 112 reduziert. Dadurch, dass das zweite Druckbegrenzungsventil 106 nur in der Saugphase der Hochdruckpumpe 101 öffnen kann, ist der Wirkungsgrad der Pumpenanordnung 100 gut.When the second pressure limiting valve 106 is open, a fluid flow from the fluid outlet 103 into the pressure chamber 104 is thus possible. 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 Injektoröffnungsdrucks. As a result, a reliable operation of the injectors 107 is made possible. In particular, the value of the opening pressure of the second pressure relief valve 106 is below the highest allowable pressure of the injector 107. Thus, the function of the injector 107 is ensured, so a reliable opening and injecting fluid into the combustion chamber. Because 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.

Die Verwendung eines passiven Druckregelventils mit vorgegebenem Wert des Öffnungsdrucks ermöglicht zudem eine Kalibrierung eines Drucksensors 123. Der Drucksensor 123 ist eingerichtet, den Fluiddruck in der Hochdrucksammelleitung 112 zu ermitteln. Der vorgegebene Wert des Öffnungsdrucks des zweiten Druckbegrenzungsventils 106 wird während des Betriebs insbesondere nicht verändert. Dadurch ist es möglich, den Drucksensor 123 gegen den fest referenzierten Wert des Öffnungsdrucks des zweiten Druckbegrenzungsventils 106 zu kalibrieren. Dies ist bei einem herkömmlich eingesetzten aktiv gesteuerten Druckregelventil nicht möglich, da der Öffnungsdruck bei einem aktiven Ventil über die angelegte Regelspannung auf unterschiedliche Werte des Öffnungsdrucks eingeregelt werden kann und somit keine feste Referenz bilden kann. Die Verwendung des passiven zweiten Druckbegrenzungsventils 106 ist auch kostengünstiger als ein herkömmlich verwendetes aktives Druckregelventil.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.

Das zweite Druckbegrenzungsventil 106 dient zum einen als Druckbegrenzungsventil, um den höchsten zulässigen Druck am Injektor 107 sicherzustellen. Zum anderen dient das Druckbegrenzungsventil 106 als Druckregelventil, um Druckpulsationen zu minimieren und insbesondere die Kalibrierung des Drucksensors 123 vorzunehmen. Die Querschnitte des zweiten Druckbegrenzungsventils 106 sind insbesondere so vorgegeben, dass eine maximal zulässige Flächenpressung trotz hoher Fluiddrücke nicht überschritten wird. Das zweite Druckbegrenzungsventil 106 ist insbesondere dauerfest ausgelegt.The second pressure relief valve 106 serves as a pressure relief valve to ensure the highest allowable pressure at the injector 107. On the other hand, 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.

Der Wert des Öffnungsdrucks des ersten Druckbegrenzungsventils 105 ist so hoch, dass Druckpulsationen während des Betriebs der Pumpenanordnung 100 nicht zum Öffnen des ersten Druckbegrenzungsventils 105 führen. Das erste Druckbegrenzungsventil 105 ist mit seiner Ausgangsseite 110 mit dem Niederdruckbereich 114 verbunden. Dadurch ist ein Druckabbau unabhängig von der Saugphase und der Druckphase der Hochdruckpumpe 101 möglich. Somit wird vermieden, dass während der Druckphase die Drücke in der Leitung größer als der Wert des Öffnungsdrucks des ersten Druckbegrenzungsventils 105 werden, was bei hydraulisch verriegelten Druckbegrenzungsventilen während der Druckphase auftreten kann. Die Querschnitte des ersten Druckbegrenzungsventils 105 sind so vorgegeben, dass bei maximalem Volumenstrom aus der Hochdruckpumpe 101 der maximal zulässige Systemdruck im Fehlerfall nicht überschritten wird. Das erste Druckbegrenzungsventil 105 ist für größere Volumenströme ausgelegt als das zweite Druckbegrenzungsventil 106.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. 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.

Somit wird sichergestellt, dass der von der Hochdruckpumpe 101 maximal geförderte Volumenstrom ohne nennenswerten Druckanstieg in der Hochdrucksammelleitung 112 wieder in den Niederdruckbereich 114 abgeführt werden kann. Ein unzulässiger Druckanstieg in der Druckphase wird vermieden. Um das erste Druckbegrenzungsventil 105 vor unzulässigem Öffnen zu schützen, wird der Wert des Öffnungsdrucks des ersten Druckbegrenzungsventils 105 oberhalb der im normalen Betrieb auftretenden Systemdrücke in der Druckphase festgelegt. Um dabei auch ein sicheres Öffnen der Injektoren 107 zu gewährleisten wird der Wert des zweiten Druckbegrenzungsventils 106 niedriger als der Wert des Öffnungsdrucks des ersten Druckbegrenzungsventils 105 vorgegeben. Somit ist die Funktion der Injektoren 107 sichergestellt. Das erste Druckbegrenzungsventil 105 öffnet nur im Fehlerfall. Da das erste Druckbegrenzungsventil 105 im Normalbetrieb nicht öffnet, wird der Verschleiß des ersten Druckbegrenzungsventils 105 verringert. Das erste Druckbegrenzungsventil 105 und das zweite Druckbegrenzungsventil 106 sind eingangsseitig hydraulisch parallel geschaltet.This ensures that the maximum flow rate that is conveyed by the high-pressure pump 101 can be dissipated again into the low-pressure region 114 without appreciable pressure increase in the high-pressure manifold 112. An impermissible pressure increase in the printing phase is avoided. In order to protect the first pressure limiting valve 105 against unauthorized opening, 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. In order to ensure a safe opening of the injectors 107, 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. Thus, the function of the injectors 107 is ensured. 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.

Figur 2 zeigt eine nicht erfindungsgemäße Pumpenanordnung 100. Die Pumpenanordnung 100 der Figur 2 entspricht im Wesentlichen den Ausführungsformen der Pumpenanordnung 100 wie in Verbindung mit Figur 1 erläutert. Im Unterschied zu den Ausführungsformen der Figur 1 ist die Ausgangsseite 111 des zweiten Druckbegrenzungsventils 106 mit dem Fluidzulauf 102 hydraulisch verbunden. 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. In contrast to the embodiments of the FIG. 1 the output side 111 of the second pressure relief valve 106 is hydraulically connected to the fluid inlet 102.

Das zweite Druckbegrenzungsventil 106 ist ausgangsseitig mit der Niederdruckseite 114 hydraulisch verbunden. Somit ist bei geöffnetem zweiten Druckbegrenzungsventil 106 ein Fluidfluss von dem Fluidablauf 103 in den Niederdruckbereich 114 möglich. Das zweite Druckbegrenzungsventil 106 ist nicht während der Druckphase der Hochdruckpumpe 101 hydraulisch verschlossen. Somit ist es möglich, dass das zweite Druckbegrenzungsventil 106 während der Druckphase der Hochdruckpumpe 101 öffnet. Dadurch werden Druckpulsationen im Fluidablauf 103 und in der Hochdrucksammelleitung 112 durch das zweite Druckbegrenzungsventil 106 minimiert. Das Totvolumen innerhalb der Hochdruckpumpe 101 wird verkleinert. Dies bewirkt eine Wirkungsgradsteigerung der Pumpenanordnung 100.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.

Figur 3 zeigt eine nicht erfindungsgemäße Pumpenanordnung 100. Die Pumpenanordnung 100 gemäß Figur 3 entspricht im Wesentlichen den Ausführungsformen wie in Verbindung mit den Figuren 1 und 2 erläutert. Im Unterschied zu den Ausführungsbeispielen der Figuren 1 und 2 ist die Eingangsseite 109 des zweiten Druckbegrenzungsventils 106 hydraulisch mit dem Druckraum 104 verbunden. Die Ausgangsseite 111 des zweiten Druckbegrenzungsventils 106 ist mit dem Fluidzulauf 102 beziehungsweise der Niederdruckseite 114 hydraulisch verbunden. 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. In contrast to the embodiments of the Figures 1 and 2 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.

Bei geöffnetem zweiten Druckbegrenzungsventil 106 ist eine Fluidfluss aus dem Druckraum 104 in den Fluidzulauf 102 freigegeben. Das zweite Druckbegrenzungsventil 106 öffnet während jeder Druckphase der Hochdruckpumpe 101. Druckpulsationen im Fluidablauf 103, in der Hochdrucksammelleitung 112 und in dem Druckraum 104 werden so minimiert.When the second pressure limiting valve 106 is open, a fluid flow from the pressure chamber 104 into the fluid inlet 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.

Figur 4 zeigt das erste Druckbegrenzungsventil 105 und das zweite Druckbegrenzungsventil 106, die hydraulisch parallel geschaltet sind. Der Wert des Öffnungsdrucks des ersten Druckbegrenzungsventils 105 ist größer eingestellt, als der Wert des Öffnungsdrucks des zweiten Druckbegrenzungsventils 106. Das erste Druckbegrenzungsventil 105 ist für größere Volumenströme ausgelegt als das zweite Druckbegrenzungsventil 106. Der Wert des Öffnungsdrucks und der Wert des maximalen Volumenstroms des ersten Druckbegrenzungsventils 105 sind so vorgegeben, dass ein maximaler vorgegebener Druck im Hochdruckbereich 115 bei funktionsfähigem ersten Druckbegrenzungsventil 105 nie überschritten wird. Der Wert des Öffnungsdrucks und der Wert des maximalen Volumenstroms des zweiten Druckbegrenzungsventils 106 sind so vorgegeben, dass ein sicheres Öffnen der Injektoren 107 gewährleistet wird so wie Druckpulsationen gedämpft werden. 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.

Figur 5 zeigt eine schematische Darstellung des zweiten Druckbegrenzungsventils 106 gemäß einem Ausführungsbeispiel. Das zweite Druckbegrenzungsventil 106 ist gemäß weiteren Ausführungsformen anders ausgebildet. 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.

Das zweite Druckbegrenzungsventil 106 ist ein sogenanntes passives Druckregelventil. Das zweite Druckbegrenzungsventil 106 weist ein Gehäuse 120 auf. In dem Gehäuse ist eine Feder 116 zwischen einem Haltelement 119 und einem Dichtelement 117 vorgespannt. Das Dichtelement 117 wird durch die Feder gegen einen Dichtsitz 118 gedrückt. Der Dichtsitz ist zwischen dem Eingang 109 und dem Ausgang 110 angeordnet. Steigt der Druck auf der Eingangsseite 109 an, wird das Dichtelement 117 gegen die Federkraft der Feder 116 vom Dichtsitz 118 wegbewegt und ein Fluidfluss von der Eingangsseite 109 zu der Ausgangsseite 110 freigegeben. An der Eingangsseite 109 ist beispielsweise ein verjüngter Querschnitt 121 vorgesehen, der zur Durchflussbegrenzung dient. Der Wert des Öffnungsdrucks des zweiten Druckbegrenzungsventils 106 wird über die Vorspannung der Feder 116 vorgegeben. Durch eine Bewegung des Halteelements 119 während der Montage des zweiten Druckbegrenzungsventils 106 entlang einer Längsachse 124 wird die Vorspannung der Feder 116 eingestellt. Erreicht die Vorspannung 116 einen vorgegebenen Wert, wird die Lage des Halteelements 119 relativ zum Gehäuse 120 fixiert. Der Wert des Öffnungsdrucks des zweiten Druckbegrenzungsventils 106 ist somit einfach vorgebbar. Durch den begrenzenden Querschnitt 121 ist eine Durchflussbegrenzung bei geöffnetem Ventil realisiert. Zudem ist einfach ein Hubanschlag für das Dichtelement 117 realisiert. Das zweite Druckbegrenzungsventil 106 ist gemäß Ausführungsformen als sogenanntes Cartridge-Ventil ausgebildet, also als eigenständiges Bauteil. Das zweite Druckbegrenzungsventil 106 ist gemäß Ausführungsformen als sogenanntes Plug-In-Ventil ausgebildet, also als Einsteckbauteil. Das zweite Druckbegrenzungsventil 106 ist gemäß Ausführungsformen direkt in ein Gehäuse der Pumpe 101 integriert.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. 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. By a movement of the holding member 119 during assembly of the second pressure relief valve 106 along a longitudinal axis 124, the bias of the spring 116 is adjusted. When 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.

Durch die Kombination des ersten und des zweiten Druckbegrenzungsventils 105, 106 in der Pumpenanordnung 100 ist es zudem möglich, den Druck auf der Hochdruckseite 115 im Betrieb im Vergleich zu herkömmlichen Systemen zu reduzieren. Somit ist es möglich, eine kostengünstige O-Ringdichtung zwischen der Hochdrucksammelleitung 112 und dem Injektor 107 vorzusehen. Somit kann auf teurere Metalldichtungen verzichtet werden. Mit der Kombination der beiden Druckbegrenzungsventile 105, 106 ist es möglich, bei einem Druck auf der Hochdruckseite 115 von bis zu 350 bar einen emissionsarmen Betrieb der Brennkraftmaschine zu ermöglichen. Bei dem Systemdruck bis zu 350 bar ist die Dichtheit der Verbindung zwischen der Hochdrucksammelleitung 112 und dem Injektor 107 über eine O-Ring sichergestellt.Moreover, by combining the 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.

Claims (8)

  1. Pump arrangement for a motor vehicle, having:
    - a high-pressure pump (101) for delivering a fluid with a fluid inlet (102) and a fluid outlet (103) and a pressure chamber (104), which is arranged hydraulically between the fluid inlet (102) and the fluid outlet (103),
    - a first pressure limiting valve (105), which is coupled on the inlet side to the fluid outlet (103),
    - a second pressure limiting valve (106), wherein
    - the two pressure limiting valves (105, 106) are connected hydraulically in parallel,
    - the two pressure limiting valves (105, 106) each have an opening pressure, wherein
    - the value of the opening pressure of the first pressure limiting valve (105) is greater than the value of the opening pressure of the second pressure limiting valve (106), and
    - the value of the opening pressure of the second pressure limiting valve (106) is predetermined depending on an injector (107), which can be coupled hydraulically to the pump arrangement (100),
    characterized in that the second pressure limiting valve (106) is coupled hydraulically on the outlet side to the pressure chamber (104).
  2. Pump arrangement according to Claim 1, in which the first pressure limiting valve (105) is coupled hydraulically on the outlet side to the fluid inlet (102).
  3. Pump arrangement according to one of Claims 1 and 2, in which the second pressure limiting valve (106) is coupled on the inlet side to the fluid outlet (103).
  4. Pump arrangement according to one of Claims 1 to 3, in which the second pressure limiting valve (106) is coupled on the inlet side to the pressure chamber (104).
  5. Pump arrangement according to one of Claims 1 to 4, in which the second pressure limiting valve (106) is designed as a passive pressure control valve with an opening pressure set to a fixed value.
  6. Pump arrangement according to one of Claims 1 to 5, in which the value of the opening pressure of the first pressure limiting valve (105) is predetermined depending on a high-pressure manifold (112) that can be coupled hydraulically between the fluid outlet (103) and the injector (107).
  7. Pump arrangement according to one of Claims 1 to 6, in which the value of the opening pressure of the second pressure limiting valve (106) is predetermined depending on the opening pressure of the injector (107).
  8. System comprising:
    - a pump arrangement (100) according to one of Claims 1 to 7,
    - a high-pressure manifold (112), which is coupled hydraulically to the fluid outlet,
    - the injector (107) for injecting the fluid into a combustion chamber of an internal combustion engine.
EP14749845.5A 2013-08-23 2014-08-11 Pump arrangement and system for a motor vehicle Active EP2932086B1 (en)

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DE102013216817.9A DE102013216817A1 (en) 2013-08-23 2013-08-23 Pump arrangement and system for a motor vehicle
PCT/EP2014/067144 WO2015024804A1 (en) 2013-08-23 2014-08-11 Pump arrangement and system for a motor vehicle

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JP (1) JP6161731B2 (en)
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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 (en) * 2015-08-18 2017-10-05 Continental Automotive Gmbh A driving method for driving a fuel injection system and fuel injection system
FR3079882B1 (en) * 2018-04-10 2020-10-16 Continental Automotive France METHOD FOR MONITORING A PRESSURE SENSOR IN A DIRECT INJECTION SYSTEM
CN109441685B (en) * 2018-10-29 2023-09-22 中船动力研究院有限公司 High-pressure common rail system of marine low-speed machine
DE102019212247A1 (en) * 2019-08-15 2021-02-18 Robert Bosch Gmbh High pressure fuel pump
CN110671224A (en) * 2019-11-08 2020-01-10 重庆红江机械有限责任公司 Low-speed machine high pressure common rail system with multiple security functions

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3939779B2 (en) * 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 Fuel supply device for fuel supply of an internal combustion engine
JPH11200990A (en) * 1998-01-07 1999-07-27 Unisia Jecs Corp Fuel injection controller
EP1411238B1 (en) * 2002-10-15 2006-01-11 Robert Bosch Gmbh Pressure regulating valve for an injection system
DE102004009792B3 (en) * 2004-02-28 2005-09-22 Daimlerchrysler Ag Fuel supply device for supplying the injectors to the combustion chambers of an internal combustion engine with fuel
DE102004013307B4 (en) * 2004-03-17 2012-12-06 Robert Bosch Gmbh High-pressure fuel pump with a pressure relief valve
DE102005033638A1 (en) * 2005-07-19 2007-01-25 Robert Bosch Gmbh Fuel conveyor, in particular for an internal combustion engine
JP4415929B2 (en) * 2005-11-16 2010-02-17 株式会社日立製作所 High pressure fuel supply pump
DE102007010502A1 (en) * 2007-03-05 2008-09-11 Robert Bosch Gmbh High-pressure fuel pump for internal-combustion engine, has pumping element for extracting fuel of suction pipe into pressure pipe, where pressure relief valve and throttle unit are connected in series in discharge line
JP5196321B2 (en) * 2008-12-26 2013-05-15 株式会社デンソー Fuel supply device and high-pressure pump
DE102009028116A1 (en) * 2009-07-30 2011-02-03 Robert Bosch Gmbh Pump, particularly high-pressure fuel pump has pressure limiting valve, where spring element of pressure limiting valve has declining characteristic
DE102010031628A1 (en) * 2009-08-17 2011-02-24 Robert Bosch Gmbh Fuel delivery device for a fuel injection device of an internal combustion engine
JP2011132941A (en) * 2009-11-26 2011-07-07 Nippon Soken Inc Pressure control valve
JP5529615B2 (en) * 2010-04-08 2014-06-25 株式会社デンソー High pressure pump
DE102010027858A1 (en) * 2010-04-16 2011-11-24 Robert Bosch Gmbh High-pressure fuel pump for an internal combustion engine
JP5158219B2 (en) * 2010-06-29 2013-03-06 株式会社デンソー Relief valve and high-pressure pump using the same
DE102010064192A1 (en) * 2010-12-27 2012-06-28 Robert Bosch Gmbh Pressure-switching valve for a fuel injection system of an internal combustion engine
DE102010064171A1 (en) * 2010-12-27 2012-06-28 Robert Bosch Gmbh Pressure control arrangement of a fuel supply system
JP5501272B2 (en) * 2011-03-08 2014-05-21 日立オートモティブシステムズ株式会社 High pressure fuel supply pump

Non-Patent Citations (1)

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

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

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