EP2659125A1 - Druckregelanordnung eines kraftstoffeinspritzsystems mit einem druckseitig von einer pumpe angeordneten ventil - Google Patents
Druckregelanordnung eines kraftstoffeinspritzsystems mit einem druckseitig von einer pumpe angeordneten ventilInfo
- Publication number
- EP2659125A1 EP2659125A1 EP11794505.5A EP11794505A EP2659125A1 EP 2659125 A1 EP2659125 A1 EP 2659125A1 EP 11794505 A EP11794505 A EP 11794505A EP 2659125 A1 EP2659125 A1 EP 2659125A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- pump
- valve
- fuel
- control arrangement
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000000446 fuel Substances 0.000 title claims abstract description 74
- 238000002347 injection Methods 0.000 title claims abstract description 31
- 239000007924 injection Substances 0.000 title claims abstract description 31
- 238000002485 combustion reaction Methods 0.000 claims abstract description 9
- 238000007599 discharging Methods 0.000 claims abstract description 4
- 230000000694 effects Effects 0.000 claims description 8
- 230000001105 regulatory effect Effects 0.000 description 10
- 230000008878 coupling Effects 0.000 description 7
- 238000010168 coupling process Methods 0.000 description 7
- 238000005859 coupling reaction Methods 0.000 description 7
- 238000000034 method Methods 0.000 description 6
- 239000000243 solution Substances 0.000 description 4
- 230000033228 biological regulation Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- 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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment
-
- 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
- F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
-
- 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
- F02M63/0045—Three-way 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
- F02M63/0012—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
- F02M63/0012—Valves
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0056—Throttling valves, e.g. having variable opening positions throttling the flow
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
- F04B49/24—Bypassing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
- F04B49/24—Bypassing
- F04B49/246—Bypassing by keeping open the outlet valve
-
- 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
- F02M2200/28—Details of throttles in fuel-injection apparatus
Definitions
- the invention relates to a pressure regulating arrangement of a pump-operated fuel injection system for an internal combustion engine, with a valve arranged on the pressure side of the pump for discharging fuel under pressure from the pressure side of the pump to the suction side of the pump. Furthermore, the invention relates to a fuel injection system with such a pressure regulating arrangement.
- the pressure is generated by means of a pump, a so-called high-pressure pump, which is mechanically driven by the internal combustion engine or engine in known fuel injection systems.
- An electromechanical, in particular electromagnetic, quantity control valve controls the quantity of fuel delivered by the pump per unit of time into a high-pressure region, a so-called rail. Together with a high pressure signal measured by a high-pressure sensor, an engine control unit thus regulates the pressure in the high-pressure range to the desired level by means of the quantity control valve.
- the control of injection valves on the internal combustion engine takes place on the basis of the measured pressure signal.
- a pressure regulating arrangement of a fuel injection system operated by a pump for an internal combustion engine having a valve for discharging fuel arranged on the pressure side of the pump under pressure from the pressure side or high pressure side of the pump to the suction side or low pressure side of the pump.
- a variable throttle On the suction side of the pump, a variable throttle is provided with a variable throttle effect, which serves to throttle the amount of fuel supplied to the pump.
- a purely self-sufficient pressure regulation is created on the pump of a fuel injection system via purely mechanical components.
- electrical, electrohydraulic or electronic components can be dispensed with.
- the invention combines two pressure control methods, namely the method of pressure control by means of the valve from the pressure range to the suction region of the pump and the method of suction throttling the pump.
- the suction throttling is preferably carried out by means of a proportional valve, which opens and closes in proportion to the applied pressure.
- the advantages of the solution according to the invention are particularly low system costs, in particular due to the elimination of otherwise required electromagnetic components.
- particularly preferred is no electromechanical quantity control valve, as is the case with known fuel injection systems.
- the energy requirement for the fuel injection according to the invention and thus the fuel consumption of the entire system due to the lack of electrical components is lower.
- the valve is advantageously functionally coupled to the variable throttle.
- the functional coupling of the valve with the variable throttle not only the pressure regulation but also the suction throttling of the pump takes place as a function of the pressure from the high-pressure region.
- the pressure from the high pressure area thus controls the valve and the variable throttle and their throttle effect.
- valve and variable throttle are preferably realized mechanically.
- the pressure or overpressure generated by the pump is advantageously applied to the valve. This means that the valve opens in particular from a certain overpressure.
- the mechanically coupled variable throttle is also adjusted.
- the pressure thus acts on the variable throttle and adjusts it.
- the valve is preferably realized as a slide valve. It advantageously captures pressure peaks coming from the high pressure area. The control with the variable throttle is thereby smoothed.
- a pressure damper function is integrated in the pressure control arrangement and it can be achieved a better control quality.
- the valve, the constant throttle and the variable throttle are preferably combined in an assembly, in particular in the pump itself.
- the conduction paths can be kept very short, which improves the dynamics of the system and at the same time saves costs.
- the weight is also reduced as compared with conventional systems.
- the assembly is easier and cheaper.
- valve and the variable throttle are realized with a single closure body.
- the valve and the variable throttle are preferably combined in one unit.
- the function of the valve and the variable throttle are then integrated into a single hydraulically controlled valve unit, in particular a proportional valve unit.
- the valve unit is designed as a piston slide valve with two control slots or control slide pairs on an associated cylinder, the function of the valve and the variable throttle being designed here in each case with a control slot.
- the closure body is preferably a piston which is resiliently biased against the pressure coming from the direction of the pump or high-pressure pump.
- the piston is in the cylinder accordingly depending on the height of the
- the closure body preferably completely covers either a first control slot or a second control slot on the cylinder.
- the control slots which take over the function of the valve and the variable throttle, are arranged offset on the cylinder of the spool valve in the axial direction. 5
- the closure body is thus preferably designed such that it can completely close only one of the two control slots, or - depending on the embodiment - at most partially covers both control slots.
- the opening movement simultaneously closes the control slot which maps the variable throttle.
- the piston closes the control slot that forms the valve and at the same time opens the second control slot, which forms the variable throttle.
- An important aspect of the design according to the invention is advantageous in that the throttle effect of the variable throttle can be varied by the pressure generated by the pump.
- the change in the throttling effect is preferably carried out in such a way that, as the pressure increases, the control slot forming the variable throttle is further closed.
- the pressure regulating arrangement designed in accordance with the invention can advantageously also be developed to have an accumulator function.
- the closure body and the control slots are designed and arranged such that the volume which releases the closure body in its movement from its rest position to reach a control slot, 0 can absorb the amount of fuel at least one cold start injection.
- the closure body moves back in the direction of its stop and replaces this amount of fuel, even if the pump has not nachge felicitt.
- the fuel pressure drops only insignificantly, depending on the spring design.
- fuel is stored in the pressure control arrangement, which is elastically stored by the spring force and the specially selected low spring rate.
- the geometries (diameter and stroke of the closure body, spring rate) of the pressure control arrangement are designed so that the storage volume is sufficient to store at least one cold start injection quantity.
- the invention is in contrast to known methods for mechanical / hydraulic pressure control. These methods are firstly the so-called (pure) pressure relief via a pressure regulating valve and secondly the so-called (pure) suction throttling.
- the pressure relief via a pressure control valve takes place when exceeding a predetermined pressure level.
- the pressure rises in principle with the amount to be eliminated. Due to the coupling of the pump speed and thus the flow rate to the engine speed, therefore, the pressure increases with the speed and falls with increasing load on the engine.
- this concept is in need of improvement, since the delivery rate of the pump is not reduced as needed and therefore higher drive performance (fuel consumption) and higher heat development is expected, especially at high speeds and low engine load (fuel cut).
- the quality of the control also has a negative effect, especially in the case of pumps with discontinuous rather full delivery in a short time large quantities must be diverted and therefore high-pressure pulsations can be stimulated.
- the supply to the pump is throttled, the higher the pressure level, so as to prevent further increase of the pressure by further pumping the pump.
- the high-pressure level is used to actuate the Saugdrosselung, relatively large forces occur on the associated variable throttle, which cause high restoring forces in the design of the throttle and therefore also lead to large return means (usually springs).
- the control quality is due to the existing dead times due to the volumes between the suction throttle and the pump, in principle, less good than the system of a pressure regulator with pressure control valve.
- the solution according to the invention makes it possible to design such fuel injection systems more cost-effectively with the same or almost the same function and to avoid the disadvantages mentioned.
- the function of said pressure control valve and the suction throttling can be combined.
- FIG. 2 shows a longitudinal section of a pressure-regulating arrangement according to the invention designed as a structural unit
- Fig. 3 is a longitudinal section of the assembly of FIG. 2 and their positioning in a high-pressure pump
- FIG. 4 shows the assembly of FIG. 3 in an enlarged view
- a fuel injection system 10 is shown with a pump 12.
- the region on the suction side of the pump 12 is referred to as the low-pressure region and the region on the pressure-side of the pump 12 as the high-pressure region.
- fuel is pumped from a tank 14 through an electric fuel pump 16 at a pressure of about 5 bar through a fuel filter 18 to a line 20.
- a pressure relief valve 22 may direct fuel from the fuel pump 16 back into the tank 14. On line 16, a low pressure damper 24 is arranged.
- the fuel delivery rate of the pump 12 is regulated by a quantity control valve 26.
- the pump 12 generates a pressure of up to about 200 bar, with which the fuel is conveyed through a Raildrossel 44 in a rail 28. This high pressure defines the already mentioned high-pressure region on the pressure side of the pump 12. From the rail 28, the fuel can be injected via injection valves 30 into an internal combustion engine 32.
- a possible overpressure of the pump 12 is derived from the high pressure area in the pump 12.
- a return line 34 which leads back into the delivery chamber of the pump 12.
- a check valve 36 mounted on the pressure side of the pump 12 forms the outlet valve of the pump 12 and prevents fuel from flowing in the opposite direction to its delivery direction.
- Another, arranged in the return line 34 check valve 38 ensures that only fuel is returned under pressure in the pump 12.
- the amount of fuel delivered by the pump 12 can be metered by the quantity control valve 26, so that the pump 12 ideally generates the setpoint control pressure.
- the pumped amount of fuel is regulated by means of a comparatively complex electromechanical system.
- a high pressure sensor 40 measures the pressure applied there.
- a controller 42 receives the information regarding the rail pressure from the high pressure sensor 40 and processes it.
- the quantity control valve 26 is activated.
- the quantity control valve 26 regulates the fuel delivery rate of the pump 12 due to the fuel pressure occurring and measured in the rail 24.
- a structural unit 72 is shown with an embodiment of the invention.
- the assembly 72 comprises an inner housing 74 on which a control slot 76, a control slot 78 and an inlet bore 80 are formed as a valve.
- the control slots 76, 78 and the inlet bore 80 are openings in the inner housing 74 which allow fuel flow into or out of the inner housing 74.
- the shape of the openings of the control slots 76, 78 preferably deviates from a rectangular or circular shape.
- the shape is preferably substantially triangular with not curved inside legs, whereby the characteristic for the pressure regulating arrangement is favorably influenced.
- the inner housing 74 designed as a piston or spool closure body 84 is slidably mounted.
- the closure body 84 is urged by a plunger 82 with respect to FIG. 2 to the left.
- the plunger 82 is formed with an intermediate portion 86 and a main portion 88. In this case, the diameter of the intermediate region 86 acting as a tappet tip or push rod is smaller than that of the closure body 84.
- the inner housing 74 is designed stepped and adapted in particular with its inner diameter to the diameter of the closure body 84. In this way, the closure body 84, the control slot 76 and / or the
- the closure body 84 can close both control slots 76, 78 at the same time.
- any overlapping or purely serial triggering of the suction throttling with the pressure relief can be achieved.
- the control quality can be optimally adjusted.
- the closure body 84 and the intermediate region 86 are made in two parts. By a convex, so an outwardly arched execution of the end of the
- the closure body 84 is biased in the inner housing 74 via the plunger 82 with a spring 90 frontally against an opposite return opening 92.
- the spring geometry of the spring 90 is dimensioned so that the transverse force minimized to the spring and thus buckling of the spring 90 is prevented.
- a seal 94 is formed in the form of a seat seal.
- a flow chamber 96 is formed in the inner housing, which is initially connected to the two control slots 76, 78, and the inlet bore 80. Depending on the respective displacement of the closure body 84 in the inner housing 74, this flow space 96 can be increased or reduced voluminously.
- the control slot 76 is connected by a parallel line 98 with the flow space 96 or the parallel line 98 can be considered as part of the flow space 96.
- FIG. 2 shows in simplified form a coupling of a pump 100, which may be driven electrically or, as is preferred, mechanically driven.
- a pump 100 With the pump 100 fuel is passed under high pressure through a pressure line 102 to a rail 104.
- the fuel Via a branch 106 in the pressure line 102, the fuel also reaches the return opening 92. Since the closure body 84 is biased against the return opening 92, initially no fuel flows into the inner housing 74. However, if the pressure which the pump 100 generates becomes too high , So this generates overpressure, the pressure force is higher than the counter-pressure force of
- the closure body 84 releases the return opening 92 and fuel can flow into the inner housing 74.
- the inflowing fuel is stored in the inner housing 74 (pressure accumulator function the arrangement).
- the closure body 84 releases the control slot 78 during this time.
- fuel conveyed by a fuel pump 108, flows via the inlet bore 80, a flow chamber 96 and the control slot 78 into a suction line 110, which leads to the pump 100.
- the closure body 84 If the pressure rises above a defined target pressure, the closure body 84 successively closes the control slot 78 and opens the control slot 76. Through the control slot 76 the fuel flows through a parallel line 98 into the flow space 96, where it mixes with the fuel from the low pressure range lo and led to the pump 100.
- control slot 76 performs the function of a valve or a pressure control valve for pressure control and the control slot 78, the function of a variable throttle or a suction throttle 15.
- the closure body 84 and the control slots 76, 78 are furthermore preferably
- the pressure control valve according to the invention prevents a possible, too large pressure drop by the fuel storage function, especially for large injection quantities in the cold start.
- the geometries (diameter and stroke of the closure body 84, spring rate of the spring 90) of the pressure regulating arrangement are designed so that the storage volume is sufficient to store at least one cold start injection quantity.
- Fig. 3 the assembly 72 of Fig. 2 in an integrative construction with the pump 100 is shown.
- the pump 100 is positioned below the assembly 72 in a common housing.
- FIG. 4 shows an enlarged detail of FIG. 3.
- the course of the fuel flow is shown here.
- the fuel flow from the fuel pump 108, through the inlet bore 80 into the flow chamber 96, and from there again through the control slot 78 in the direction of the pump 100 shown (suction pressure, low pressure region).
- the fuel flow is shown with a solid arrow line, which is first performed by the pump 100 to the rail 104 (high-pressure area).
- a positive pressure is passed through the branch 106 to the return opening 92 and displaces the closure body 84.
- the return opening 92 is opened and the fuel continues to the control slot 76, and from there through the parallel line 98 to the flow space 96.
- the recirculated fuel unites with the from the inlet of the fuel pump 108. If the pressure drops below the setpoint control pressure again, then the closure body 84 shifts to the left with respect to the figure and opens the control slot 78 for suction throttling and closes the control slot 76 for pressure control. Or, in other words, as soon as the force of the spring 90 is sufficient to push the closure body 84 back against the decreasing force of the overpressure.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE201010064219 DE102010064219A1 (de) | 2010-12-27 | 2010-12-27 | Druckregelanordnung eines Kraftstoffeinspritzsystems mit einem druckseitig von einer Pumpe angeordneten Ventil |
PCT/EP2011/072829 WO2012089511A1 (de) | 2010-12-27 | 2011-12-14 | Druckregelanordnung eines kraftstoffeinspritzsystems mit einem druckseitig von einer pumpe angeordneten ventil |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2659125A1 true EP2659125A1 (de) | 2013-11-06 |
EP2659125B1 EP2659125B1 (de) | 2014-09-17 |
Family
ID=45319125
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11794505.5A Not-in-force EP2659125B1 (de) | 2010-12-27 | 2011-12-14 | Druckregelanordnung eines kraftstoffeinspritzsystems mit einem druckseitig von einer pumpe angeordneten ventil |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2659125B1 (de) |
CN (1) | CN103270289B (de) |
DE (1) | DE102010064219A1 (de) |
WO (1) | WO2012089511A1 (de) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2550144A (en) * | 2016-05-10 | 2017-11-15 | Delphi Automotive Systems Lux | Fuel pump |
CN106321309A (zh) * | 2016-08-26 | 2017-01-11 | 重庆凯龙科技有限公司 | 压力侧设有节流部的燃油调节泵 |
CN106321311B (zh) * | 2016-08-30 | 2018-10-12 | 重庆凯龙科技有限公司 | 带有弹簧振动装置的燃油调节泵 |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH672168A5 (de) * | 1987-01-30 | 1989-10-31 | Nova Werke Ag | |
DE4323683A1 (de) * | 1993-07-15 | 1995-01-19 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe |
JP3304755B2 (ja) * | 1996-04-17 | 2002-07-22 | 三菱電機株式会社 | 燃料噴射装置 |
JP4453028B2 (ja) * | 2005-03-30 | 2010-04-21 | 株式会社デンソー | 高圧燃料ポンプ |
JP2008057451A (ja) * | 2006-08-31 | 2008-03-13 | Hitachi Ltd | 高圧燃料供給ポンプ |
DE102008043217A1 (de) * | 2008-10-28 | 2010-04-29 | Robert Bosch Gmbh | Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine |
DE102008058288A1 (de) * | 2008-11-20 | 2010-05-27 | Continental Mechanical Components Germany Gmbh | Druckbegrenzungsventil und Hochdruckpumpe mit einem Druckbegrenzungsventil |
-
2010
- 2010-12-27 DE DE201010064219 patent/DE102010064219A1/de not_active Withdrawn
-
2011
- 2011-12-14 EP EP11794505.5A patent/EP2659125B1/de not_active Not-in-force
- 2011-12-14 CN CN201180062377.4A patent/CN103270289B/zh not_active Expired - Fee Related
- 2011-12-14 WO PCT/EP2011/072829 patent/WO2012089511A1/de active Application Filing
Non-Patent Citations (1)
Title |
---|
See references of WO2012089511A1 * |
Also Published As
Publication number | Publication date |
---|---|
CN103270289A (zh) | 2013-08-28 |
EP2659125B1 (de) | 2014-09-17 |
DE102010064219A1 (de) | 2012-06-28 |
CN103270289B (zh) | 2016-05-04 |
WO2012089511A1 (de) | 2012-07-05 |
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