EP3036430A1 - Device for a high-pressure pump for a motor vehicle - Google Patents
Device for a high-pressure pump for a motor vehicleInfo
- Publication number
- EP3036430A1 EP3036430A1 EP15733401.2A EP15733401A EP3036430A1 EP 3036430 A1 EP3036430 A1 EP 3036430A1 EP 15733401 A EP15733401 A EP 15733401A EP 3036430 A1 EP3036430 A1 EP 3036430A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- actuator assembly
- actuator
- valve
- volume body
- valve housing
- 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
- 239000007787 solid Substances 0.000 claims abstract description 14
- 239000012530 fluid Substances 0.000 claims description 48
- 238000007789 sealing Methods 0.000 claims description 3
- 238000013016 damping Methods 0.000 description 20
- 238000000034 method Methods 0.000 description 6
- 230000008569 process Effects 0.000 description 6
- 238000011161 development Methods 0.000 description 5
- 230000018109 developmental process Effects 0.000 description 5
- 238000012546 transfer Methods 0.000 description 5
- 239000000446 fuel Substances 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 238000013461 design Methods 0.000 description 3
- 235000021251 pulses Nutrition 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 230000000875 corresponding effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000002347 injection Methods 0.000 description 2
- 239000007924 injection Substances 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 235000010627 Phaseolus vulgaris Nutrition 0.000 description 1
- 244000046052 Phaseolus vulgaris Species 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- 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
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
- F02M59/366—Valves being actuated electrically
-
- 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
- F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
-
- 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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0027—Pulsation and noise damping means
- F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
-
- 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
- F02M2200/09—Fuel-injection apparatus having means for reducing noise
-
- 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
-
- 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
- F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
- F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means
Definitions
- the present invention relates to a device for a high-pressure pump for a motor vehicle, which is suitable for keeping vibrations and noise developments through valves small.
- solenoid actuated valves are used to control fluid flow. These valves are usually adjusted in the axial direction to adjust a flow area and provide a required amount of fluid, especially fuel.
- This move moving components due to space constrained to limiting elements that are deliberately introduced constructive, for example, to limit a stroke of the moving parts of the valve.
- a pulse is transmitted, which leads to vibrations and scattered over the high pressure pump can be reproduced as sound and possibly perceived as a disturbing noise.
- a device for a high-pressure pump for a motor vehicle comprises a valve housing, a central axis and an actuator assembly, which is arranged substantially along the central axis in the valve housing.
- the actuator assembly in this case has an Aktoraus quietlyung, starting from a first end of the actuator assembly in the Actuator assembly extends.
- the actuator assembly has at least one hydraulic compensation opening, which penetrates a wall of the actuator assembly from the Aktorausappelung to an outdoor area.
- the device has a volume body, which is arranged in the AktorausEnglishung spaced from the Aktorbau devise and extending into a region of the at least one hydraulic compensation opening. In this case, the volume body is arranged immovably relative to the valve housing, while the
- Valve housing and is arranged axially movable relative to the volume body.
- a device for a high-pressure pump for a motor vehicle which is adapted during an operation of the motor vehicle to keep vibration and noise ⁇ development by valves low.
- a controlled hydraulic damping is achieved during operation of the power ⁇ vehicle, which makes it possible to reduce an impulse upon impact of moving components of the valve to adjacent optionally rigidly mounted components, so as to reduce vibrations and Geisseschent ⁇ developments.
- the hydraulic damping is achieved by the volume body in the valve housing, which is arranged relative to the valve housing as a non-movable component of the device in the valve housing and selectively changes a cross section and a volume for a fluid flowing through.
- the flowing fluid passes, for example, in the valve housing and from there through the at least one hydraulic compensation opening in the region of Aktorausappelung.
- the valve is opened or closed, fluid flows in or out of the actuator recess, allowing hydraulic damping to continue as it progresses.
- the actuator assembly may be formed as a single element, for example in one piece, or may comprise a plurality of components, which are connected to each other, for example, positively, force and / or cohesively.
- the hydraulic damping described, which is achieved by the bean ⁇ spruchte device is, as described, achieved by the solid, which is rigidly arranged as an additional component of the valve in the valve housing.
- Movable components of the device such as the Aktorbaueria
- the volume body as a rigidly arranged component of the valve, it is simply possible to passively achieve a hydraulic damping of the fluid flowing through, without having to actively set, for example, a hydraulic damping.
- Active hydraulic damping is achieved, for example, in the case of a magnetic valve in that an actuator is energized and counter-energized in order to to mitigate such an impact on neighboring components. This inevitably requires additional electrical power and leads to an increased consumption of the motor vehicle, which is avoided for example by means of the device described.
- a number of the hydraulic compensation opening is not limited to one and can be scaled arbitrarily in this context, so that the at least one or more hydraulic compensation openings penetrate the wall of the actuator assembly and connect the Aktoraus originallyung with the outer region of the actuator assembly.
- a geometry of the at least one hydraulic compensation opening is variable and can be formed space-related. For example, it is advantageous if a plurality of hydraulic equalization holes are drilled in the wall of the actuator assembly.
- a geometry of the volume body is arbitrarily scalable due to space constraints, so that at least ensures that the volume body is arranged spaced from the movable components of the valve and during operation of the power ⁇ vehicle not in contact with these and that a controlled change in the volume takes place is traversed by the fluid.
- Aktoraus quietlyung are arranged, which fulfill the functions just described.
- the actuator assembly comprises an actuator and a valve needle, which in an operating state in cooperation with a sealing seat fluid flow of a fluid in a closed position of the
- Actuator assembly prevents and otherwise releases.
- the actuator of the actuator assembly on the Aktorausappelung and the at least one hydraulic compensation opening is formed in the We ⁇ sentlichen between the actuator and the valve needle.
- the volume body is arranged in the AktorausEnglishung spaced from the actuator and projects in an opening ⁇ or closing process in the region of at least one hyd ⁇ raulischen compensation opening, so that, for example, the moving valve needle of the actuator assembly approaches the solid or away from it.
- the actuator of the actuator assembly includes, for example, an anchor or can also be called an anchor itself.
- the first aspect of the solid body is formed substantially cylindrical.
- the volume body is designed rotationally symmetrical, which allows, for example, in connection with a fluid flowing through during operation of the motor vehicle, a homogeneous flow pattern and thereby a controlled hydraulic damping.
- the solid body extends substantially along the central axis or is arranged at least substantially parallel to the middle axis.
- the actuator, the valve needle and the Aktorausströmung the actuator assembly are rotationally symmetrical and arranged axially relative to the central axis and thus realized in a simple and symmetrical manner controlled trolling the moving actuator and the moving valve needle, before this example on the Ven ⁇ tilgephaseuse meets.
- the device comprises a pole piece, which is arranged adjacent to the actuator of the actuator assembly and by means of which
- Actuator is magnetically apparent or closable.
- the volume body extends substantially from the first end of the actuator assembly into the region of the at least one hydraulic compensation opening.
- a magnetically actuated valve for controlling the fluid flow in which a controlled hydraulic damping of the flowing fluid and the moving components of the valve is achieved by the arranged volume.
- the moving meets
- the solid is cohesively and / or non-positively and / or positively coupled to the pole piece.
- This embodiment of the device shows ways in which the solid body can be arranged rigidly and immovably in the valve housing.
- the volume body and the pole piece are welded together, glued or clamped and so together immovably arranged in the valve housing, while the actuator and the valve needle of the actuator assembly are arranged axially movable in the valve housing relative to the volume body and the pole piece.
- the pole piece has a Polaus Principleung in which the solid is partially arranged.
- the first aspect of the solid body is formed integrally with the pole piece.
- a high ⁇ pressure pump comprises a device according to the first aspect.
- FIG. 1 shows a schematic representation of a high-pressure pump
- Figures 2A-2B an embodiment of an outwardly öff ⁇ nenden valve in the open position
- Figures 3A-3B an embodiment of an outwardly open ⁇ nenden valve in the closed position.
- FIG. 1 schematically shows a high-pressure pump 30 which has, inter alia, a fluid supply line 33.
- the fluid supply line 33 is hydraulically coupled to a cylinder space 31.
- the high-pressure pump 30 also has a fluid drain 35.
- the cylinder chamber 1 is arranged hydraulically between the fluid supply line 33 and the fluid discharge line 35.
- the high-pressure pump 30 is in particular a high-pressure pump for a fuel injection system for internal combustion engines of motor vehicles.
- a pump housing 32 of the high pressure pump 30 surrounds the Zylin ⁇ derraum 1 and the fluid supply line 33 to the cylinder chamber 31, and the fluid discharge 35. During a suction phase of the high pressure pump 30 fluid is sucked through the fluid supply line 33 into the cylinder chamber 31 from a low pressure region.
- the fluid supply line 33 is hydraulically coupled by means of a feed pump (not explicitly shown) to a fluid tank (not explicitly shown).
- a valve 1 is arranged, which controls an inlet of the fluid into the cylinder chamber 31.
- the fluid in the cylinder chamber 31 is subjected to a pressure, for example by a piston movement in the cylinder chamber.
- the pressurized with the pressure fluid is discharged from the cylinder chamber 31 through an outlet valve by means of the Fluidab ⁇ line 35 from the high-pressure pump 30.
- the fluid discharge line 35 is coupled to a rail of a common rail injection system.
- the high pressure pump 30 is configured, for example, pressures of up to 2000 bar or more _
- FIGS. 2A and 2B show, in cross section, an exemplary structure of the valve 1 which is magnetically actuable and which comprises a valve housing 3, a central axis 17 and an actuator assembly 5.
- the Aktorbauxx 5 is arranged relative to the central axis 17 in the valve housing 3 axially movable relative to the valve housing 3 and has in this exemplary embodiment ⁇ an actuator 7 and a valve needle 9, during an operation of the valve 1 in cooperation with a sealing seat 16th a fluid flow of a fluid in a closed ⁇ position of the actuator assembly 5, consisting of actuator 7 and valve needle 9, prevents and otherwise releases.
- the actuator 7 of the actuator assembly 5 includes, for example, an armature or may itself be referred to as an anchor.
- a pole piece 21 and a spring 19 are arranged, which realize an opening and closing process of the valve 1.
- the spring 19 exerts a spring force on the actuator assembly 5 and thereby pushes the actuator 7 of the actuator assembly 5 away from the pole piece 21.
- the valve 1 Without energizing the pole piece 21, d. H. without applying a voltage to a magnetic coil 211, which is wound around the pole piece 21, the valve 1 is thus permanently open. If the pole piece 21, that is, the winding coil 211 energized, a magnetic closing of the valve 1 is made possible by a magnetic force generated by the energization of the pole piece 21 outweighs the spring force and the actuator 7 of the
- Actuator assembly 5 accelerates in the direction of the pole piece 21.
- the valve 1 described here is, as already described, normally open.
- the valve 1 may also be designed so that it is normally closed.
- the actuator 7 of the actuator assembly 5 has, in the region of a first end 6 of the actuator assembly 5, an actuator recess 11 which extends into the actuator assembly 5 and in which, inter alia, part of the spring 19 is arranged.
- the pole piece 21 has a Polausströmauerung 23, in which the spring 19 extends. Hydraulic off ⁇ equal openings 13 are formed between the actuator 7 and the valve needle 9, which during the operation of the valve 1, the fluid flow from an outer region 12 of the
- a volume body 15 is arranged, which extends into a region 14 of the hydraulic compensation openings 13.
- the volume body 15 for example, non-positively connected to the pole piece 21 and was the
- the volume body 15 has a substantially cylindrical shape and has a wider cylindrical recess in the pole recess 23 and a narrower cylindrical body in the form of a pin in the actuator recess 11.
- the solid 15 may have other geometric shapes.
- FIG. 2B the region 14 of the hydraulic compensation openings 13 of the valve 1 is shown in detail.
- the fluid for example a fuel
- the valve 1 flows into the valve 1 and the valve housing 3 and reaches the area 14 of the hydraulic compensation openings 13.
- the fluid flows through the hydraulic compensation openings 13 and thus enters the Aktoraus originallyung 11 of the actuator 7 of the actuator assembly 5.
- the fluid flows around the volume body 15 and the spring 19, so that a flow pattern of the fluid is influenced by the volume body 15.
- the volume body 15 changes a volume accessible to the fluid in the region 14 of the hydraulic
- Figure 3A shows the valve 1 in a cross section in the ge ⁇ closed position in which the mass element 15 in the area
- the volume 15 has the Cross-section and the volume in the region 14 of the hydraulic equalization openings 13 changed and thereby specifically influences an outflow of the fluid from the Aktoraus foundedung 11.
- a controlled hydraulic damping is achieved, which brakes a movement of the actuator 7 in the direction of the pole piece 21 and thereby reduces a Aufschchskraft and a pulse ⁇ transfer to the pole piece 21 and / or the valve housing 3. This has the advantage that the formation of vibrations and noise is counteracted.
- the fluid flowing through has less volume when flowing out of the actuator recess 11 through the hydraulic compensation openings 13, so that the movement of the actuator assembly 5 is influenced by a throttled movement of the fluid.
- FIG. 3B shows the valve 1 shown in FIG. 3A in the closed position with a detailed view of the area 14 of the hydraulic compensation openings 13.
- This volume change has a corresponding effect on a subsequent opening process of the valve 1, so that due to the volume body 15, for example, the movement of the valve needle 9 is attenuated when opening the valve 1 for the reasons described and the AufSchlagskraft and the momentum transfer are reduced.
- the valve 1 shown in Figures 2A, 2B, 3A and 3B thus allows in a simple manner by the rigidly arranged volume body 15, a hydraulic damping of the moving Components of the valve 1, such as the actuator 7 and the valve needle 9 of the actuator assembly 5 in an opening and closing process of the valve 1.
- movably arranged components of the valve 1 are not changed, so that, for example, a mass of the actuator assembly. 5 remains unchanged.
- An arrangement of the volume body 15, for example, on the actuator assembly 5 may also lead to a damping of movement of the actuator assembly 5, but also due to the increase in the mass moved to an increased pulse, which in turn reduces the effect of a desired hydraulic damping.
- the hydraulic damping by means of the volume body 15 is achieved substantially passively, since the volume body 15 is arranged immovably as a rigid component of the valve 1, for example relative to the valve housing 3. Active hydraulic damping is achieved, for example, in the case of a magnetic valve in that the pole piece 21 is energized and counter-energized so as to attenuate the impact of the actuator 7 on the pole piece 21 or the impact of the valve needle 9 against the valve housing 3. This inevitably requires additional elekt ⁇ generic performance and leads to an increased consumption of the motor vehicle.
- a further beneficial effect is achieved, characterized in that the spring 19 is arranged around the volume body 15.
- the volume body 15 has in this way also a spring-guiding effect, since the spring 19 is guided on an inner diameter of the volume body 15.
- a number of the hydraulic compensation openings 13 is not limited and can be arbitrary in this context be scaled so that the at least one or more hydraulic compensation openings 13, the wall of the
- a geometry of the at least one hydraulic From ⁇ equal opening 13 is variable and can be formed due to installation space. For example, it is advantageous if several hyd ⁇ raulische compensation openings 13 through the wall of the
- Actuator 5 are drilled.
- a geometry of the volume body 15 is arbitrarily scalable due to space constraints, so that at least ensures that the volume body 15 spaced from movable components of the valve 1, such as the actuator 7 and the valve needle 9 of the
- Actuator assembly 5 is arranged and during an operation of the motor vehicle not in contact with these.
- the volume body 15 always carries out a controlled change in the volume in the region 14 of the hydraulic compensation openings 13, through which the fluid flows during operation of the motor vehicle.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Magnetically Actuated Valves (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102014215774.9A DE102014215774B4 (en) | 2014-08-08 | 2014-08-08 | Device for a high-pressure pump for a motor vehicle |
PCT/EP2015/064306 WO2016020106A1 (en) | 2014-08-08 | 2015-06-24 | Device for a high-pressure pump for a motor vehicle |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3036430A1 true EP3036430A1 (en) | 2016-06-29 |
EP3036430B1 EP3036430B1 (en) | 2018-02-28 |
Family
ID=53498983
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15733401.2A Not-in-force EP3036430B1 (en) | 2014-08-08 | 2015-06-24 | Device for a high-pressure pump for a motor vehicle |
Country Status (7)
Country | Link |
---|---|
US (1) | US9903357B2 (en) |
EP (1) | EP3036430B1 (en) |
JP (1) | JP6084340B2 (en) |
KR (1) | KR101922315B1 (en) |
CN (1) | CN105723083B (en) |
DE (1) | DE102014215774B4 (en) |
WO (1) | WO2016020106A1 (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014215774B4 (en) | 2014-08-08 | 2016-06-30 | Continental Automotive Gmbh | Device for a high-pressure pump for a motor vehicle |
EP3364015B8 (en) * | 2017-02-15 | 2020-06-03 | Vitesco Technologies GmbH | Electromagnetic switching valve and high-pressure fuel pump |
DE102020202429A1 (en) | 2020-02-26 | 2021-08-26 | Hyundai Motor Company | Digital inlet valve for a system for direct gasoline injection in a motor vehicle |
DE102020206494A1 (en) | 2020-05-25 | 2021-11-25 | Hyundai Motor Company | Fuel pump for a liquid fuel-water injection system of a motor vehicle |
DE102020206493A1 (en) | 2020-05-25 | 2021-11-25 | Hyundai Motor Company | Fuel pump for a liquid fuel injection system of a motor vehicle |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3510222A1 (en) * | 1985-03-21 | 1986-09-25 | Robert Bosch Gmbh, 7000 Stuttgart | SOLENOID VALVE, ESPECIALLY FUEL VOLUME CONTROL VALVE |
US4821774A (en) * | 1988-04-04 | 1989-04-18 | Chorkey William J | Solenoid operated valve with balancing means |
DE4137994C2 (en) * | 1991-11-19 | 1999-06-02 | Bosch Gmbh Robert | Electromagnetically actuated injection valve with a nozzle holder and method for producing a nozzle holder of an injection valve |
DE102004028886A1 (en) * | 2004-06-15 | 2006-01-05 | Robert Bosch Gmbh | Fuel injection system |
DE102006036780A1 (en) * | 2006-08-07 | 2008-02-21 | Robert Bosch Gmbh | Fuel injector with direct needle control and servo valve support |
DE102009046079A1 (en) * | 2009-10-28 | 2011-05-12 | Robert Bosch Gmbh | Valve for quantity control of a fuel high pressure pump, comprises a valve element and a stop on which the valve element comes in opened condition in plant, and a damping device with a movable piston limiting a fluid chamber |
DE102010061793A1 (en) * | 2009-12-29 | 2011-06-30 | Robert Bosch GmbH, 70469 | Electromagnetically actuated switching valve, in particular quantity control valve in particular for controlling the delivery rate of a high-pressure fuel pump |
DE102011089288A1 (en) | 2011-12-20 | 2013-06-20 | Robert Bosch Gmbh | Flow control valve, and high pressure pump with flow control valve |
DE102012211394A1 (en) | 2012-07-02 | 2014-01-02 | Robert Bosch Gmbh | Metering unit for fuel pump i.e. high pressure pump, of fuel injection system for air-compressing, self-igniting internal combustion engine, has valve body actuated indirectly by actuator and transition case made of plastic material |
DE102012218593A1 (en) | 2012-10-12 | 2014-04-17 | Continental Automotive Gmbh | Valve for a pump |
DE102014215774B4 (en) | 2014-08-08 | 2016-06-30 | Continental Automotive Gmbh | Device for a high-pressure pump for a motor vehicle |
-
2014
- 2014-08-08 DE DE102014215774.9A patent/DE102014215774B4/en not_active Expired - Fee Related
-
2015
- 2015-06-24 CN CN201580002658.9A patent/CN105723083B/en not_active Expired - Fee Related
- 2015-06-24 JP JP2016535177A patent/JP6084340B2/en not_active Expired - Fee Related
- 2015-06-24 KR KR1020167016929A patent/KR101922315B1/en active IP Right Grant
- 2015-06-24 US US15/031,372 patent/US9903357B2/en not_active Expired - Fee Related
- 2015-06-24 EP EP15733401.2A patent/EP3036430B1/en not_active Not-in-force
- 2015-06-24 WO PCT/EP2015/064306 patent/WO2016020106A1/en active Application Filing
Non-Patent Citations (1)
Title |
---|
See references of WO2016020106A1 * |
Also Published As
Publication number | Publication date |
---|---|
US20170261115A1 (en) | 2017-09-14 |
KR101922315B1 (en) | 2018-11-26 |
KR20160089493A (en) | 2016-07-27 |
DE102014215774B4 (en) | 2016-06-30 |
JP2017501328A (en) | 2017-01-12 |
WO2016020106A1 (en) | 2016-02-11 |
JP6084340B2 (en) | 2017-02-22 |
CN105723083B (en) | 2018-10-16 |
DE102014215774A1 (en) | 2016-02-11 |
CN105723083A (en) | 2016-06-29 |
US9903357B2 (en) | 2018-02-27 |
EP3036430B1 (en) | 2018-02-28 |
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