CN104508293A - High-pressure pump for internal combustion engines - Google Patents
High-pressure pump for internal combustion engines Download PDFInfo
- Publication number
- CN104508293A CN104508293A CN201380040401.3A CN201380040401A CN104508293A CN 104508293 A CN104508293 A CN 104508293A CN 201380040401 A CN201380040401 A CN 201380040401A CN 104508293 A CN104508293 A CN 104508293A
- Authority
- CN
- China
- Prior art keywords
- valve
- armature
- closure body
- pressure
- pump
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/20—Output circuits, e.g. for controlling currents in command coils
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/30—Controlling fuel injection
- F02D41/38—Controlling fuel injection of the high pressure type
- F02D41/3809—Common rail control systems
- F02D41/3836—Controlling the fuel pressure
- F02D41/3845—Controlling the fuel pressure by controlling the flow into the common rail, e.g. the amount of fuel pumped
-
- 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
- F02M59/368—Pump inlet valves being closed when actuated
Abstract
The invention relates to a suction valve (2) which is used for a high-pressure pump (1), which is used in particular for air-compressing, self-igniting internal combustion engines. The suction valve (2) comprises a valve closing body (15), which interacts with a sealing seat (13), and an armature (30), which can be magnetically actuated and which is connected to the valve closing body (15). A pressure stage is provided, by means of which the valve closing body (15) can be loaded in an opening direction (28). Furthermore, the armature (30) can be magnetically actuated in such a way that the valve closing body (15) can be loaded against the sealing seat (13) in the closing direction (33) by a magnetic closing force by means of the armature (30). Furthermore, a high-pressure pump (1) having such a suction valve (2) is specified. By means of this embodiment, the activation energy for the suction valve (2) can be reduced.
Description
Technical field
The present invention relates to a kind of suction valve for high-pressure service pump, this high-pressure service pump is particularly useful for internal-combustion engine that is compressed-air actuated, self ignition, and relates to a kind of high-pressure service pump, especially radial piston pump or tandem piston pump.But this high-pressure service pump also can as the liquid of reciprocating pump for carrying other suitable.
Background technique
By the known a kind of high-pressure service pump of DE 10 2,010 027 745A1, it is especially used for the fuel injection apparatus of the internal-combustion engine of compressed-air actuated, self ignition as radial piston pump or tandem piston pump.Be provided with at this and enter valve, can measure by it the fuel be transported in pump working chamber.The completely filled of pump working chamber can be realized at this.But the part that also can realize pump working chamber by suitably controlling to enter valve fills.Realize handling by electromagnetic coil energising.This especially in electromagnetic coil power-off time valve spring power can cause the closedown entering valve to a great extent without delay.At this, valve spring acts on armature by valve element and adjustment plate, and armature is connected with valve follower.Therefore, valve follower is loaded by the pretightening force of valve spring.Valve spring is towards valve seat surface charge valve push rod.
Therefore, in the high-pressure service pump known by DE 10 2,010 027 745A1, enter valve by manipulation and fuel can be made to be transported to pump working chamber from low pressure chamber.At this, the manipulation entering valve is carried out during the suction stroke of pump piston.During the delivery stroke of pump piston, enter that valve preferably cuts out.What realize thus closing in no current state enters valve.High closedown can be realized dynamic by the corresponding high initial tension of spring of valve spring.But the defect of the program is, open to make to enter valve and stay open, electromagnetic coil must be energized.Just under closing dynamic high initial tension of spring situation for height, need corresponding strong magnetic field, this brings big current and brings large power loss thus.Therefore, in known scheme, produce large control energy, must stay open because enter valve at whole sucting stage.
Summary of the invention
The advantage of the high-pressure service pump of the present invention of the suction valve of the present invention with the feature of claim 1 and the feature with claim 8 it is possible to the metering controlling fuel better.Especially can reduce energy consumption and thus reduce required control energy.
The favourable improvement to the high-pressure service pump provided in the suction valve provided in claim 1 and claim 8 can be realized by the measure provided in the dependent claims.
By pressure steps, valve closure body can be loaded in the direction of the opening.On the closing direction against opening direction orientation, valve closure body is loaded by magnetic closing forces by armature.Therefore, this magnetic closing forces is for supporting the closedown of suction valve.Cause closing movement preferably by the such degree of magnetic closing forces, make suction valve enter throttling by not throttle.Then by hydraulic coupling support closure or even cause closedown at least to a great extent in throttling.Therefore, advantageously no longer must magnetic closing forces at the end of closing process.Improve the manipulation of suction valve thus.The power drain and the required control energy that are particularly useful for closedown reduce.
Advantageously, the guiding diameter for leading to valve closure body is less than the seat diameter of sealing seat.Thus, described pressure steps can be loaded according to prime discharge pressure with effective power in the direction of the opening.Thus when prime discharge pressure corresponding large and pressure simultaneously in pump working chamber reduces there is opening of suction valve based on pressure proportional, fuel is transported in pump working chamber through the sealing seat opened.
At this also advantageously, described valve closure body is connected with armature by coupling bar (bibcock), described coupling bar is directed in the pilot hole with guiding diameter, further, form a valve chamber between pilot hole and sealing seat, the fuel be under prime discharge pressure can be channeled in this valve chamber, armature is arranged in armature chamber, this armature chamber is separated with valve chamber by the bibcock be directed in pilot hole, and described armature chamber is release with regard to prime discharge pressure.Therefore, the prime discharge pressure of the fuel in valve chamber advantageously can cause effective power in the direction of the opening, but, with the pressure correlation in pump working chamber, power in the closing direction and aforementioned power points on the contrary.But during the suction stroke of the pump piston of high-pressure service pump, pressure in pump working chamber reduces, and makes the breaking force formed in summation in the direction of the opening, this power makes to be in fuel under prime discharge pressure can in inflow pump working room.
Advantageously can be provided with valve spring, it loads valve closure body at least indirectly in the closing direction.At this also advantageously, described valve spring is arranged in the armature chamber at armature place, and/or described valve spring loads valve closure body by armature and/or bibcock, and this bibcock makes armature be connected with valve closure body.Described closedown spring limits the initial position of suction valve on the one hand.Spring constant and given pretightening force on the other hand by selecting closedown spring can produce in the closing direction along with skew and thus the spring force risen along with opening stroke.This makes it possible to coordinate suction valve.
In addition advantageously, be provided with control gear, it causes electromagnetically-operated to armature by making electromagnetic coil be energized during the shutoff stroke of valve closure body, and wherein, this control gear makes electromagnetic coil be transformed into no current before sealing seat is closed completely.It reduce required manipulation energy.Also the cooling requirement being used for electromagnetic coil is reduced thus.At this also advantageously, control gear carrys out control valve closure body, until realize throttling on sealing seat by making electromagnetic coil energising during the shutoff stroke of valve closure body.If realize throttling on sealing seat, then further shutoff stroke can purely mechanically be closed by chamber pressure in the rising of pump working chamber.
Therefore, it is possible to advantageously in the suction stroke of pump mounting assembly (pressure reduce) in the trip in pump working chamber by acting on prime discharge pressure on described pressure steps and control valve closure body in the direction of the opening.In addition, if by making valve closure body be handled by such degree in the closing direction to the electromagnetically-operated of armature, so that on sealing seat, realize throttling, then can (pressure in the trip in pump working chamber raises) valve closure body be handled in the closing direction by the pressure in pump working chamber in the delivery stroke of pump mounting assembly.
Accompanying drawing explanation
Explain the present invention in detail by accompanying drawing in the following description, corresponding element is provided with unified reference character in the accompanying drawings.Accompanying drawing illustrates:
Fig. 1 according to one embodiment of the present of invention, the local constructed profile map of the high-pressure service pump with suction valve,
Fig. 2 for explaining the plotted curve according to the high-pressure service pump of one embodiment of the present of invention and the functional mode of suction valve,
Fig. 3 for explaining another plotted curve according to the high-pressure service pump of this embodiment of the present invention and the functional mode of suction valve,
Fig. 4 is for explaining another plotted curve according to the high-pressure service pump of this embodiment of the present invention and the functional mode of suction valve.
Embodiment
Fig. 1 illustrates the high-pressure service pump 1 according to one embodiment of the invention with local schematic profile.This high-pressure service pump 1 especially can be configured to radial piston pump or tandem piston pump.This high-pressure service pump 1 is particularly suitable as the fuel injection apparatus of petrolift for the internal-combustion engine of compressed-air actuated, self ignition.High-pressure service pump 1 has suction valve 2.This suction valve 2 is particularly suitable to be used in this high-pressure service pump 1.But according to suction valve 2 of the present invention when corresponding change adaptedly be also applicable to other application.
The advantageous applications of this high-pressure service pump 1 and suction valve 2 is the fuel injection apparatus with fuel distribution lath, and this fuel distributes the diesel oil under lath storage high pressure.But also can be controlled by suction valve 2 and carry other liquid be applicable to by high-pressure service pump 1, namely other is as the liquid of fuel.
High-pressure service pump 1 has cylinder head 3, forms the pump working chamber 4 of pump mounting assembly 5 wherein.At this, form cylinder holes 6 in cylinder head 3, pump piston 7 is directed in this cylinder holes.Pump piston 7 is gauge pump working chamber 4 in cylinder holes 6.The live axle 8 with cam 9 is supported with in this external unshowned housing.Be in operation, live axle 8 rotates around its spin axis 10.By cam 9, the manipulation to pump piston 7 occurs at this, this is indicated by double-head arrow 11.This manipulation can such as be undertaken by the roller be bearing in roller boots.
Suction valve 2 has valve body 12, and valve body forms sealing seat 13.Sealing seat 13 is configured with a diameter 14 in this embodiment circularly.This is provided with valve closure body 15, sealing seat 13 acting in conjunction of it and valve body 12.
Valve body 12 is fixed on cylinder head 3 by closed screw.Formed between valve body 12 and cylinder head 3 at this and seal, make pump working chamber 4 high pressure resistant relative to environment seal.
Suction valve 2 has valve chamber 20, is carried the fuel be under prime discharge pressure by one or more hole 21,22 in this valve chamber.Closure body 15 abuts in side under valve in off position to be had on the sealing seat 13 of a diameter 14.In addition, valve closure body 15 is connected with bibcock 23 or forms integratedly with this bibcock.Bibcock 23 is directed in the pilot hole 24 of matrix 25 that can be configured to magnetic core.Pilot hole 24 has guiding diameter 26 at this, and this guiding diameter is less than the seat diameter 14 of sealing seat 13.Bibcock 23 extend in armature chamber 27, and this armature chamber is release relative to the prime discharge pressure in valve chamber 20.Therefore mineralization pressure ladder, this pressure steps is determined by the seat diameter 14 of sealing seat 13 and the guiding diameter 26 of pilot hole 24.Therefore, based on prime discharge pressure, this pressure steps produces the power pointed to along the axis 29 of bibcock 23 to opening direction 28.
Suction valve 2 also has armature 30, and this armature is connected with bibcock 23 and is arranged in armature chamber 27.This is outside equipped with electromagnetic coil 31, and it can be energized by control gear 32.When electromagnetic coil 31 is energized, this electromagnetic coil produces magnetic force on armature 30, and valve closure body 15 is loaded by the direction of the sealing seat 13 towards valve body 12 on the closing direction 33 pointed to against opening direction 28 thus.
Also be provided with valve spring 34 in this embodiment, it is loaded on closing direction 33 by armature 30 and bibcock 23 pairs of valve closure bodies 15.
Below also with reference to Fig. 2,3 and 4 configuration and the functional modes that high-pressure service pump 1 and suction valve 2 be described.Fig. 2,3 and 4 illustrate that one for explaining the plotted curve of the functional mode of high-pressure service pump 1 and suction valve 2 respectively.Mark the stroke of valve closure body in opening direction 28 in fig. 2 on the horizontal scale at this, and mark the flow relevant to stroke on the vertical scale.Mark the stroke of valve closure body 15 in opening direction 28 in figure 3 on the horizontal scale, and mark the power acted on closing direction 33 on valve closure body 15 on the vertical scale.Mark the time on the horizontal scale in the diagram, and mark pressure in pump working chamber 4, the stroke of valve closure body 15 in opening direction 28 and the energising of electromagnetic coil 31 on the vertical scale.
In fig. 2 curve 40 is illustratively shown, it indicates between valve closure body 15 and sealing seat 13 from valve chamber 20 to the flow 40 pump working chamber 4.When stroke is more than a value 41, then suction valve 2 is in not throttling procedure, and this is represented by region 42 in fig. 2.Under value 41, suction valve 2 is in throttling, and this is represented by region 43.When stroke disappears, flow 40 also disappears.
In order to interpretation maps 3, from state 44s, in a state in which, suction valve 2 is in without reaching relatively large, the especially maximum stroke of valve closure body 15 in this region in throttling band 42.Described the possible change trend of the spring force of valve spring 34 by curve 45, this spring force acts on valve closure body 15 on closing direction 33.Curve 45 illustrates with the y coordinate intersection point 46 of y coordinate the pretightening force do not disappeared.The pretightening force of valve spring 44 can suitably be selected at this.The slope of curve 45 also can be given in advance by the spring constant of valve spring 34.In state 44, first substantially apply reposition force by valve spring 34.If allow this point (being such as this situations when the delivery stroke of pump piston 7) with the pressure dependence in pump working chamber 4 in valve chamber 20, then namely valve closure body 15 closes based on the reposition force of valve spring 34, first curve 47 is continued near curve 45, and wherein curve continuity direction is represented by arrow 47.In region 48, by control gear 32, electromagnetic coil 31 is energized.Thus, closing direction 33 acts on the precipitous rising of closing forces on valve closure body 15, and this is represented by arrow 49.Thus, valve closure body 15 applies maximum, force 50.At this, lower than value 41, suction valve 2 is arrived in throttling band 43.Continue to reduce at this trip, this is represented by arrow 51.At the end of electromagnetic coil 31 is energized (this represents by region 48), suction valve 2 has been in throttling band 43.Therefore, further closing forces can be applied by the pressure of the increase of valve spring 34 and pump working chamber 4 in region 52.When stroke disappears (now suction valve 2 in other words valve seat 13 be close), be maintained by the closing forces given by y coordinate intersection point 53 of curve 47 and y coordinate.This closing forces is produced by the pretightening force of valve spring 34 and described pressure steps.Therefore, y coordinate intersection point 43 depends on prime discharge pressure (prime operating pressure).
Therefore produce the region 48 of relative narrower, need electromagnetic coil 31 to be energized in this region.Therefore, power drain obviously reduces.
Time interval 48' shown in Figure 4,48 ", in these intervals, electromagnetic coil 31 is energized.Therefore, 54 are energized by having representing with the curve 54 at the edge declined of rising rapidly.
The pressure in pump working chamber 4 is represented by curve 55.This pressure respectively at time interval 48', 48 " in rise, wherein, support the closedown of suction valve 2 in throttling band 43 respectively by the pressure of the rising in pump working chamber 4.After suction valve 2 cuts out, pressure continues to rise, and this is caused by the delivery stroke of pump piston 7.Curve 56 represents the change trend of the stroke of valve closure body 15.In order to simplify view, curve 54,55,56 from a common level, and wherein, in this level, initial value is not be necessary for zero.
Therefore, suction valve 2 is configured to valve 2 that outwards open, that have pressure steps.If the interior chamber pressure in pump working chamber 4 is less than the prime discharge pressure before suction valve 2, then valve closure body 15 is opened against valve spring 34.Pump working chamber 4 is filled, until suction valve 2 by the energising of electromagnetic coil 31 by electrically never throttle pull out.Further shutoff stroke is then pure mechanically to be realized, because suction valve 2 is in throttling by the interior chamber pressure of the rising of pump working chamber 4.Therefore, advantageously under little stroke situation of change, obtain the extremely short manipulation time, for activating the closing movement of suction valve 2.
Therefore, determine according to the configuration of suction valve 2 or control gear 32, region 48 also can comprise original state 44.The closedown of the suction valve 2 then direct energising by electromagnetic coil 31 causes.
The present invention is not limited to described embodiment.
Claims (10)
1. for the suction valve (2) of high-pressure service pump (1), this high-pressure service pump is particularly useful for compressed-air actuated, the internal-combustion engine of self ignition, this suction valve has a valve closure body (15) coefficient with sealing seat (13) and has and is connected with valve closure body (15), the armature (30) of Electromagnetically activatable, it is characterized in that, be provided with pressure steps, by this pressure steps, valve closure body (15) can be loaded in opening direction (28), and, described armature (30) can by such electromagnetically-operated, described valve closure body (15) is loaded towards described sealing seat (13) by a magnetic closing forces by described armature (30) on closing direction (33).
2. suction valve as claimed in claim 1, it is characterized in that, the guiding diameter (26) for leading to valve closure body (15) is less than the seat diameter (14) of described sealing seat (13).
3. suction valve as claimed in claim 2, it is characterized in that, described valve closure body (15) is connected with armature (30) by bibcock (23), described bibcock (23) is directed in the pilot hole (24) with guiding diameter (26), valve chamber (20) is formed between pilot hole (24) and sealing seat (13), the fuel be under prime discharge pressure can be transported in this valve chamber, armature (30) is arranged in armature chamber (27), this armature chamber is separated with valve chamber (20) by the bibcock (23) be directed in pilot hole (24), and, described armature chamber (27) is release with regard to described prime discharge pressure.
4. suction valve as claimed any one in claims 1 to 3, is characterized in that, be provided with valve spring (34), and this valve spring loads described valve closure body (15) at least indirectly on closing direction (33).
5. suction valve as claimed in claim 4, it is characterized in that, described valve spring (34) is arranged in the armature chamber (27) at armature (30) place, and/or, described valve spring (34) loads valve closure body (15) by armature (30) and/or bibcock (23), and this bibcock makes armature (30) be connected with valve closure body (15).
6. the suction valve according to any one of claim 1 to 5, it is characterized in that, be provided with control gear (32), this control gear causes electromagnetically-operated to armature (30) by making electromagnetic coil (31) be energized during the shutoff stroke of valve closure body (15), wherein, described control gear (32) makes electromagnetic coil (31) be transformed into no current before sealing seat (13) is closed completely.
7. suction valve as claimed in claim 6, it is characterized in that, described control gear (32) handles described valve closure body (15), until realize throttling on sealing seat (13) by making electromagnetic coil (31) be energized during the shutoff stroke of valve closure body (15).
8. high-pressure service pump (1), in particular for radial piston pump or the tandem piston pump of the fuel injection apparatus of the internal-combustion engine of compressed-air actuated, self ignition, there is at least one cylinder head (3), there is pump mounting assembly (5), this pump mounting assembly is included in the pump working chamber (4) formed in cylinder head (3), this high-pressure service pump also has at least one suction valve (2) according to any one of claim 1 to 7, wherein, can by fuel area density in pump working chamber (4) by the sealing seat (13) of described suction valve (2).
9. high-pressure service pump as claimed in claim 8, it is characterized in that, pressure in the suction stroke of described pump mounting assembly (5) in pump working chamber (4) reduces, in this suction stroke, made it possible to the described valve closure body (15) of the upper manipulation of opening direction (28) by the prime discharge pressure acted on described pressure steps.
10. high-pressure service pump as claimed in claim 8 or 9, it is characterized in that, pressure in the delivery stroke of described pump mounting assembly (5) in pump working chamber (4) raises, in this delivery stroke, if by making valve closure body (15) be handled by with this degree on closing direction (33) to the electromagnetically-operated of armature (3), so that realize throttling on sealing seat (13), then described valve closure body (15) is above handled at closing direction (33) by the pressure in pump working chamber (4).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102012213546.4 | 2012-08-01 | ||
| DE102012213546.4A DE102012213546A1 (en) | 2012-08-01 | 2012-08-01 | High pressure pump for internal combustion engines |
| PCT/EP2013/065587 WO2014019904A1 (en) | 2012-08-01 | 2013-07-24 | High-pressure pump for internal combustion engines |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104508293A true CN104508293A (en) | 2015-04-08 |
| CN104508293B CN104508293B (en) | 2018-07-03 |
Family
ID=48856630
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380040401.3A Expired - Fee Related CN104508293B (en) | 2012-08-01 | 2013-07-24 | For the high-pressure pump of internal combustion engine |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP2880297B1 (en) |
| CN (1) | CN104508293B (en) |
| DE (1) | DE102012213546A1 (en) |
| IN (1) | IN2014DN10748A (en) |
| WO (1) | WO2014019904A1 (en) |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6167870B1 (en) * | 1997-01-27 | 2001-01-02 | Komatsu Ltd. | Control device and control method for cam driving type electronic control unit injector |
| DE102008018018A1 (en) * | 2008-04-09 | 2009-10-15 | Continental Automotive Gmbh | Pump for conveying a fluid |
| CN101994575A (en) * | 2009-08-18 | 2011-03-30 | 德尔福技术控股有限公司 | Control method for common rail fuel pump and apparatus for performing the same |
| WO2011104907A1 (en) * | 2010-02-26 | 2011-09-01 | 日立オートモティブシステムズ株式会社 | High pressure fuel pump |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102010027745A1 (en) | 2010-04-14 | 2011-10-20 | Robert Bosch Gmbh | high pressure pump |
| DE102010039832A1 (en) * | 2010-08-26 | 2012-03-01 | Continental Automotive Gmbh | Method and device for detecting reaching a closing point of a hydraulic valve |
-
2012
- 2012-08-01 DE DE102012213546.4A patent/DE102012213546A1/en not_active Withdrawn
-
2013
- 2013-07-24 WO PCT/EP2013/065587 patent/WO2014019904A1/en active Application Filing
- 2013-07-24 CN CN201380040401.3A patent/CN104508293B/en not_active Expired - Fee Related
- 2013-07-24 EP EP13740010.7A patent/EP2880297B1/en active Active
-
2014
- 2014-12-16 IN IN10748DEN2014 patent/IN2014DN10748A/en unknown
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6167870B1 (en) * | 1997-01-27 | 2001-01-02 | Komatsu Ltd. | Control device and control method for cam driving type electronic control unit injector |
| DE102008018018A1 (en) * | 2008-04-09 | 2009-10-15 | Continental Automotive Gmbh | Pump for conveying a fluid |
| CN101994575A (en) * | 2009-08-18 | 2011-03-30 | 德尔福技术控股有限公司 | Control method for common rail fuel pump and apparatus for performing the same |
| WO2011104907A1 (en) * | 2010-02-26 | 2011-09-01 | 日立オートモティブシステムズ株式会社 | High pressure fuel pump |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2014019904A1 (en) | 2014-02-06 |
| EP2880297A1 (en) | 2015-06-10 |
| CN104508293B (en) | 2018-07-03 |
| IN2014DN10748A (en) | 2015-09-04 |
| DE102012213546A1 (en) | 2014-02-06 |
| EP2880297B1 (en) | 2020-10-07 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101029695B (en) | Electromagnetic actuator performing quick response | |
| US7013872B2 (en) | Fuel injector for internal combustion engine | |
| US8677977B2 (en) | Direct injection pump control strategy for noise reduction | |
| US8882475B2 (en) | Electromagnetic flow rate control valve and high-pressure fuel supply pump using the same | |
| EP2055931B1 (en) | Plunger type high-pressure fuel pump | |
| KR101652678B1 (en) | Valve for injection of gas | |
| US20090199820A1 (en) | Pressure control valve with limp-home and ventilation function | |
| US20030145810A1 (en) | Engine valve actuator providing miller cycle benefits | |
| JPH11218065A (en) | Solenoid control fuel injection device | |
| JPH04501594A (en) | Valve control device equipped with a solenoid valve used in internal combustion engines | |
| CN103180601B (en) | Pressure regulator valve | |
| US9181890B2 (en) | Methods of operation of fuel injectors with intensified fuel storage | |
| KR20190091351A (en) | Method for providing variable compression ratio of internal combustion engine and actuator used in the method | |
| US7007644B2 (en) | System and method for preventing piston-valve collision on a non-freewheeling internal combustion engine | |
| CN102537483B (en) | Decompressor | |
| CN104508293A (en) | High-pressure pump for internal combustion engines | |
| US9441594B2 (en) | Valve actuator assembly with current trim and fuel injector using same | |
| JP2005517118A (en) | Fuel injection device used for internal combustion engine | |
| KR101654752B1 (en) | Valve for injection of gas | |
| JPH11201000A (en) | Fuel injection system reinforced its tip member | |
| US6688291B2 (en) | High-pressure fuel supply system | |
| US6817324B2 (en) | Control unit of electromagnetically driven valve and control method thereof | |
| KR102232823B1 (en) | Fuel injector with msm element | |
| US6467462B2 (en) | Fuel injection system for internal combustion engines | |
| CN215761843U (en) | Timing unit of exhaust valve driver of marine two-stroke diesel engine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| EXSB | Decision made by sipo to initiate substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20180703 Termination date: 20210724 |