EP2855919B1 - Druckregelventil - Google Patents
Druckregelventil Download PDFInfo
- Publication number
- EP2855919B1 EP2855919B1 EP13718167.3A EP13718167A EP2855919B1 EP 2855919 B1 EP2855919 B1 EP 2855919B1 EP 13718167 A EP13718167 A EP 13718167A EP 2855919 B1 EP2855919 B1 EP 2855919B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- flow
- valve
- closing element
- valve seat
- pressure regulating
- 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
Links
- 230000001105 regulatory effect Effects 0.000 claims description 14
- 238000007373 indentation Methods 0.000 claims 3
- 239000000446 fuel Substances 0.000 description 5
- 230000008878 coupling Effects 0.000 description 4
- 238000010168 coupling process Methods 0.000 description 4
- 238000005859 coupling reaction Methods 0.000 description 4
- 238000002485 combustion reaction Methods 0.000 description 3
- 239000000243 solution Substances 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 238000002347 injection Methods 0.000 description 2
- 239000007924 injection Substances 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000005465 channeling Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000001681 protective effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Images
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
- 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
- F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
- F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
-
- 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
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/042—The valves being provided with fuel passages
-
- 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
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
- F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
-
- 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
- F02M63/0043—Two-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
- F02M63/0052—Pressure relief valves with means for adjusting the opening pressure, e.g. electrically controlled
-
- 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
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
- F02M63/0073—Pressure balanced 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
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
- F02M63/0077—Valve seat details
Definitions
- a pressure control valve in which the pressure control valve is open when the internal combustion engine is at a standstill, which means that a connection from the high-pressure accumulator to a low-pressure line is released by a closing element.
- the pressure regulating valve has a magnetic actuator that is energized to close the closing element, in which an armature places the closing element in a valve seat.
- a spring element is provided which acts against the magnetic force of the magnetic actuator and thereby moves the armature and an armature bolt attached to it in the opening direction. This lifts the closing element off the valve seat and releases a hydraulic return connection between the high-pressure accumulator and the low-pressure line.
- the hydraulic return connection to the low-pressure line takes place from a valve chamber downstream of the valve seat, from which bores branching off radially to the side are provided, which open into a low-pressure line in the housing of the high-pressure accumulator.
- DE 10 2010 043 097.7 and the U.S. 5,549,274 A also relates to a pressure control valve.
- This serves to open or close a drain of a high pressure accumulator for an injection device for internal combustion engines and comprises a valve element.
- This is operated by a solenoid actuator.
- the solenoid actuator acts by means of an armature on a closing element which closes or releases a hydraulic connection from the high-pressure accumulator to a valve chamber.
- the anchor plate comprises an anchor plate and an anchor bolt and is axially movably guided in a valve housing.
- the anchor plate is movably arranged in an anchor space.
- the valve chamber is hydraulically connected to a low-pressure connection.
- the armature chamber is hydraulically connected to the valve chamber via a return connection.
- a pressure control valve in the form of a solenoid valve is known that is used to control an injection valve of an internal combustion engine, the Solenoid valve, an electromagnet, a movable armature, a control valve member moved with the armature and interacting with a valve seat for opening and closing a fuel drain channel of a control pressure chamber.
- the fuel flow flowing towards the spherically designed closing element be impressed with a clear flow path in order to stabilize the flow around the spherically designed closing element.
- a clear flow path it must be ensured that the flow separates at the end of the seat and comes into contact with the ball. This is achieved in that a sharp edge opening outward is formed at the end of the seating area.
- the opening angle of the outwardly opening edge at the end of the seat area is in the order of magnitude of approximately 20 ° larger compared to the valve seat angle. Ideally, the opening angle is approx. 180 °.
- an outflow is created in the axial direction which absorbs the flow from a wrap angle of about 120 °.
- the ball stop is designed either as a spherical cap or as a cone, so that the spherical closing element is fixed in position accordingly and the forces required to keep the spherical closing element securely closed can be transmitted at a given high pressure level.
- the fluid is drained off at the end of the axial bores with an angle piece.
- a throttle can be integrated into this elbow, which in an alternative embodiment can also be located at the end of the central bore. By means of this throttle element, returning pressure waves can be kept away from the valve.
- a hydraulic connection preferably made up of a 90 ° connection, already prevents part of the coupling of returning pressure waves, since the pressure waves are automatically reflected within the elbow.
- Both plunger anchors and flat anchors can be used as actuators for actuating the closing element proposed according to the invention.
- the decisive factor for the design of the magnet is its characteristic curve, which, in conjunction with the hydraulic valve characteristic curve, ensures the greatest possible stability of the pressure control valve or of its spherical closing element.
- the solution proposed according to the invention can ensure that the fuel flow is applied to the spherical surface of the preferably spherical closing element and thus the hydraulic forces acting on the spherical closing element can be kept constant in the area of its operating point.
- the force action in relation to the hydraulic forces on the closing element or on the valve member that actuates it, which is usually designed in the form of a pin is not subject to fluctuations since the force balance remains essentially unchanged.
- instabilities in particular noises and pressure waves in the pressure control valve, can be avoided.
- the mentioned instabilities are disadvantageous for the low-pressure circuit connected to the pressure control valve and if not completely eliminated by the solution proposed according to the invention, then at least greatly reduced.
- a pressure control valve 10 which comprises a valve body 12.
- a magnetic actuator 16 which in the embodiment according to Figure 1 is designed for example as a magnetic coil. This is electrically contacted via an electrical contact 14, which is integrated in a protective cap of the pressure control valve 10.
- the valve body 12 of the pressure control valve 10 as shown in FIG Figure 1 comprises an outlet 18 via which the return flow from a cavity 20 into a low-pressure side Return area is controlled.
- Figure 1 shows an anchor-shaped valve member 22, which is embodied in the form of a pin and which acts on a closing element 24, extends through the valve body 12. Via the valve member 22, the closing element 24 is placed in a valve seat 26 which, when the valve seat 26 is closed, closes an outlet throttle 28. So that no fuel can flow out via the outlet throttle 28 into the cavity 20 and thus into the outlet 18 on the low pressure side.
- the illustrated state is the closing element 24, which is spherical, shown in its closed position. That is, the valve seat 26 is closed.
- Figure 2 shows, on an enlarged scale, the forces that act on a spherically designed closing valve of a pressure control valve.
- FIG. 2 shows that when the closing element 24 is open, a drainage flow 40 is established between a spherical surface 34 of the closing element 24 and the surface delimiting the valve seat 26.
- a valve seat diameter 36 identified by reference numeral 36
- two different flow paths 30 and 32 of the outflow flow 40 are established.
- a first flow path 30 of the drainage flow 40 runs along the surface of the valve seat 26, while a drainage flow 40 is established according to a second flow path 32, which partially follows the spherical surface 34 of the spherically designed closing element 24.
- the valve seat 26 is formed at an opening angle 56.
- the opening angle 56 here denotes the angle at which the valve seat 26 is formed.
- the opening angle 56 which is also referred to as the seat angle, is a maximum of 90 °. If the opening angle 56 is measured in relation to the opposite seat surface of the valve seat 26, it can be a maximum of 180 °.
- an opening angle 58 which is also in relation to the axis of symmetry 38 as well as to the in Figure 3 opposite side of the valve seat 26, not shown, can be defined.
- the surface which runs at the opening angle 56 is adjoined by an edge 54 which opens sharply outward and which can also be referred to as a tear-off edge.
- the opening angle 58 by which the edge 54, which is sharply opened outward, adjoins the end zone 42 of the valve seat 26, is denoted by reference numeral 58 and is preferably 20 ° more than the seat angle of the valve seat 26.
- Edge 54 ie the tear-off edge 54, 90 ° in relation to the axis of symmetry 38 of the in Figure 3 illustrated valve seat design according to the invention.
- the edge 54 which opens sharply outward, ensures that the discharge flow 40, which flows out of the discharge throttle 28, becomes a detaching flow 44 in relation to the surface of the valve seat 26, which in turn rests against the spherical surface 34 of the closing element 24. So that the applied flow 46 as shown in FIG Figure 3 remains on the spherical surface 34, in a development according to the invention at least one axially extending outflow channel 50 is provided.
- the at least one channel 50 runs parallel to the axis of symmetry 38 of the discharge throttle 28 and the space in which the valve seat 26 is formed. From the representation according to Figure 3 It can be seen that the spherically designed closing element 24 is held in the open state by a dome-like arrangement 48.
- the at least one outflow duct 50 which extends coaxially to the axis of symmetry 38, is formed in this dome-shaped arrangement 48.
- the outflow channel 50 is preferably designed as a bore and in a preferred embodiment of the invention, several smaller outflow channels 50, for example 3, are arranged symmetrically distributed over the circumference in the dome-like arrangement 48, so that the entire amount diverted when the valve seat 26 is fully open can be diverted into a central bore 52 on the low-pressure side.
- an applied flow 46 is established, which covers a wrap angle 76 between 90 ° and 150 °, in particular by 120 °, with respect to the spherical surface 34 of the closing element 24.
- the applied flow 46 separates from the closing element 24 and flows - as in FIG Figure 3 exemplified - in the outflow channel 50 a.
- a flow cross-section 60 of the at least one outflow channel 50 in the dome-like arrangement 48 is preferably selected so that each individual outflow channel 50 acts as a throttle, the total area of all flow cross-sections 60 of all outflow channels 50 being sufficient for the complete transfer of the controlled return flow into the central bore 52.
- valve member in this variant is designed as a plunger 68 which is acted upon by a spring 70.
- the dome-shaped arrangement 48 which encloses the spherically designed closing element 24.
- the outflow channels 50 are shown in the plunger 68, through which the diverted quantity flows into the central bore 52 when the valve seat 26 is open.
- the central bore 52 goes - apart from the transition into the valve body - in an angle piece 62, which represents a 90 ° connection of the return area.
- at least one throttle element 66 can be provided, via which the controlled return flow rate is throttled.
- Reference numeral 14 indicates the electrical contact via which the magnetic actuator 16 - shown here as a magnetic coil - is controlled for actuating the plunger 68 in this embodiment variant.
- Reference numeral 60 denotes the flow cross section of the outflow channels 50
- reference numeral 54 denotes the edge on the valve seat 26 that opens sharply outward.
- FIG. 5 the variant of a pressure control valve proposed according to the invention using a flat armature with a spring is shown.
- a flat anchor 72 is used Insert which is acted upon by a spring element 70.
- the flat anchor 72 according to the illustrated embodiment knows Figure 5 the dome-shaped arrangement 48 on its side facing the closing element 24.
- the forces which act on the valve member, which is designed here as a flat armature 72 when the magnetic actuator 16 is actuated are transmitted to the closing element 24.
- the outflow channels 50 two of which are shown here in cross section, are located in the end face of the flat armature 72, which lies opposite the spherical closing element 24.
- the amount controlled is passed via the outflow channels 50 into the central bore 52, and from there via at least one throttle element 66 into the area already described above in connection with Figure 4 mentioned 90 ° connection 64 shown here as an elbow 62.
- the diverted amount takes place at the end of the central bore 52 in the elbow 62.
- a throttle element 66 is arranged at the end of the central bore 52 or in the elbow 62 is irrelevant.
- the arrangement given by the 90 ° connection 64 also partially prevents a coupling of returning pressure waves, since these are reflected within the angle piece 62 and can no longer be transmitted into the central bore 52 and consequently no longer represent a source of interference.
- FIG. 6 a variant of the pressure control valve proposed according to the invention is shown, which comprises a plunger with a closing spring.
- valve member is designed as a plunger 68.
- the plunger 68 is acted upon by a closing spring 74, which is supported on the valve body of the pressure control valve 10.
- the closing element designed as a plunger 68 is pressed into its closed position via the closing spring 74, so that the valve element 24 closes the valve seat 26 and thus the outlet throttle 28.
- the dome-shaped arrangement 48 is formed, via which the forces of the plunger 68 are transmitted to the spherical closing element 24.
- FIG. 6 shows that the magnetic actuator in this embodiment is designed as a magnetic coil 16, which can be energized via an electrical contact 14.
- Position 54 denotes the edge on valve seat 26 that opens sharply outward.
- the flat armature 72 is traversed by the central bore 52 and acted upon in the closing direction by the closing spring 74, the closing spring 74 being supported on the valve body of the pressure control valve 10.
- the dome-shaped arrangement 48, on which the outflow channels 50 are formed, is located on the end face of the flat armature 72, which is opposite the spherical closing element 24.
- control quantities flowing out of the outlet throttle 28 are conducted into the central bore 52 via the outflow channels 50.
- the throttle element 66 can also be shown in the angle piece 62, which in this variant forms the 90 ° connection 64 will.
- the 90 ° connection 64 in all variants of the Figures 4 to 7 also partially prevents a coupling in of returning pressure waves, which are reflected in the angle piece 62 of their own accord.
- Figure 8 shows a further embodiment of the valve seat proposed according to the invention.
- At least one outflow channel 50 is designed in an enlarged flow cross section 60 downstream of the spherical closing element 24, at least one outflow channel 50 is designed in an enlarged flow cross section 60.
- the flow cross section 60 in the at least one outflow channel 50 according to the variant embodiment Figure 8 much larger, so that the end face of the spherical cap 48 on which the spherical closing element 24 is opened when the Valve seat 26 is applied, is minimized and the flow cross section 60 is large enough.
- the cross-sectional area of the at least one outflow channel 50 through which there is flow extends in the axial direction and has no radial component, so that no pressure gradients can occur in the radial direction, ie perpendicular to the outflow direction.
- a separation point at which the flow applied to the spherical surface 34 dissolves is approximately 120 °, which means that the outlet flow 40 leaving the outlet throttle 28 in a wrap angle 76 in the order of between 90 ° and 120 ° on the spherical surface 34 of the Closing element 24 rests before it detaches in the axial direction.
- the at least one outflow channel 50 opens into the central bore 52 in an enlarged flow cross-section 60.
- the geometry of the valve seat 26 is also essentially identical with regard to the tear-off edge 54 which is sharply bent radially at the opening angle 58 from the opening angle 56 of the valve seat 26.
- Also in the variant embodiment of the valve seat 26 proposed according to the invention according to FIG Figure 8 relieves the flow 44 detaching from the valve seat 26 in the end zone 42 of the valve seat 26, which is manufactured in the valve seat diameter 36.
- the plunger 68 is supported on a resilient element 80, in particular designed as a C-ring, on the valve body 12.
- the resilient element 80 in particular represented by a C-ring, also offers the possibility of channeling the discharge flow 40 exiting via the discharge throttle 28 into the flow channels 50 when the valve seat 26 is open, that is to say to separate or separate the main flow from the secondary volumes surrounding the plunger 68. to seal.
- both plunging anchors 68 and flat anchors 72 can be used.
- the characteristic curve which, together with the hydraulic characteristic curve of the pressure regulating valve 10 proposed according to the invention, ensures the greatest possible stability in the operation of the pressure regulating valve 10 is decisive for the design.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Magnetically Actuated Valves (AREA)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102012209226A DE102012209226A1 (de) | 2012-05-31 | 2012-05-31 | Druckregelventil |
PCT/EP2013/058096 WO2013178402A1 (de) | 2012-05-31 | 2013-04-18 | Druckregelventil |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2855919A1 EP2855919A1 (de) | 2015-04-08 |
EP2855919B1 true EP2855919B1 (de) | 2020-10-28 |
Family
ID=48170461
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13718167.3A Active EP2855919B1 (de) | 2012-05-31 | 2013-04-18 | Druckregelventil |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP2855919B1 (zh) |
CN (1) | CN104364510B (zh) |
DE (1) | DE102012209226A1 (zh) |
IN (1) | IN2014DN07381A (zh) |
WO (1) | WO2013178402A1 (zh) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014215442A1 (de) * | 2014-08-05 | 2016-02-11 | Robert Bosch Gmbh | Druckregelventil mit integriertem Drucksensor |
DE102015111813B4 (de) * | 2015-07-21 | 2017-03-02 | Kendrion (Villingen) Gmbh | Sitzventil |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10052604A1 (de) * | 2000-10-24 | 2002-05-02 | Bosch Gmbh Robert | Magnetventil zur Steuerung eines Einspritzventils einer Brennkraftmaschine |
DE102013211924A1 (de) * | 2013-06-24 | 2014-12-24 | Robert Bosch Gmbh | Druckregelventil mit Führung im Ventilkörper |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3010612A1 (de) * | 1980-03-20 | 1981-10-01 | Robert Bosch Gmbh, 7000 Stuttgart | Elektromagnetisch betaetigbares ventil |
US5549274A (en) * | 1994-04-20 | 1996-08-27 | Cummins Engine Company, Inc. | Ball guide for an electronically actuated control valve |
JP2003176765A (ja) * | 2001-12-11 | 2003-06-27 | Denso Corp | コモンレール式燃料噴射システム |
DE102004002964A1 (de) * | 2004-01-21 | 2005-08-11 | Robert Bosch Gmbh | Druckregelventil für einen Hochdruckspeicher einer Verbrennungskraftmaschine |
DE102007054496B4 (de) * | 2006-11-14 | 2013-03-14 | Hydraulik-Ring Gmbh | Hochdruckventil für Dieseleinspritzanlagen mit Gleichdruckverhalten |
DE102007053649B3 (de) * | 2007-11-08 | 2009-05-07 | Hydraulik-Ring Gmbh | Druckregelventil |
DE102008043841A1 (de) * | 2008-11-19 | 2010-05-20 | Robert Bosch Gmbh | Kugelventil für Hochdruckpumpen |
DE102009027575A1 (de) * | 2009-07-09 | 2011-01-13 | Robert Bosch Gmbh | Schaltventil |
DE102010043097A1 (de) | 2010-10-29 | 2012-05-03 | Robert Bosch Gmbh | Druckregelventil |
-
2012
- 2012-05-31 DE DE102012209226A patent/DE102012209226A1/de not_active Withdrawn
-
2013
- 2013-04-18 EP EP13718167.3A patent/EP2855919B1/de active Active
- 2013-04-18 WO PCT/EP2013/058096 patent/WO2013178402A1/de unknown
- 2013-04-18 CN CN201380028885.XA patent/CN104364510B/zh not_active Expired - Fee Related
-
2014
- 2014-09-02 IN IN7381DEN2014 patent/IN2014DN07381A/en unknown
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10052604A1 (de) * | 2000-10-24 | 2002-05-02 | Bosch Gmbh Robert | Magnetventil zur Steuerung eines Einspritzventils einer Brennkraftmaschine |
DE102013211924A1 (de) * | 2013-06-24 | 2014-12-24 | Robert Bosch Gmbh | Druckregelventil mit Führung im Ventilkörper |
Also Published As
Publication number | Publication date |
---|---|
EP2855919A1 (de) | 2015-04-08 |
WO2013178402A1 (de) | 2013-12-05 |
DE102012209226A1 (de) | 2013-12-05 |
IN2014DN07381A (zh) | 2015-04-24 |
CN104364510A (zh) | 2015-02-18 |
CN104364510B (zh) | 2017-11-28 |
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