CN104508293B - For the high-pressure pump of internal combustion engine - Google Patents
For the high-pressure pump of internal combustion engine Download PDFInfo
- Publication number
- CN104508293B CN104508293B CN201380040401.3A CN201380040401A CN104508293B CN 104508293 B CN104508293 B CN 104508293B CN 201380040401 A CN201380040401 A CN 201380040401A CN 104508293 B CN104508293 B CN 104508293B
- Authority
- CN
- China
- Prior art keywords
- valve
- closure body
- pressure
- armature
- 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.)
- Expired - Fee Related
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 8
- 239000000446 fuel Substances 0.000 claims description 16
- 238000002347 injection Methods 0.000 claims description 4
- 239000007924 injection Substances 0.000 claims description 4
- 230000009467 reduction Effects 0.000 claims description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 claims 2
- 229910052742 iron Inorganic materials 0.000 claims 1
- 230000000630 rising effect Effects 0.000 description 4
- 230000008878 coupling Effects 0.000 description 3
- 238000010168 coupling process Methods 0.000 description 3
- 238000005859 coupling reaction Methods 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 2
- 230000003213 activating effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000011159 matrix material Substances 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
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
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Magnetically Actuated Valves (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
One kind is used for the inlet valve (2) of high-pressure pump (1), and the high-pressure pump is particularly for compressed air, self-ignition internal combustion engine.Armature (30) that the inlet valve (2) is connect including valve closure body (15) coefficient with seal receptacle (13) and with valve closure body (15), Electromagnetically activatable.It is provided with pressure steps herein, by it, valve closure body (15) can be loaded in opening direction (28).In addition the armature (30) can be by electromagnetically-operated so that the valve closure body (15) by armature (30) by magnetic closing forces in closing direction (33) towards seal receptacle (13) load.Also propose a kind of high-pressure pump (1) with this inlet valve (2).It can be reduced with this solution for the manipulation energy of inlet valve (2).
Description
Technical field
The present invention relates to a kind of suction valves for high-pressure pump, and the high-pressure pump is particularly for compressed air, self-ignition
Internal combustion engine, and be related to a kind of high-pressure pump, especially radially piston pump or tandem piston pump.But the high-pressure pump can also be used as work
Plug pumps to convey other suitable liquid.
Background technology
A kind of high-pressure pump as known to 10 2,010 027 745A1 of DE, it is especially as radial piston pump or tandem piston pump
For the fuel injection apparatus of compressed air, self-ignition internal combustion engine.It is provided with herein into valve, can be measured by it defeated
The fuel being sent in pump working chamber.The complete filling of pump working chamber can be realized herein.But it can also be entered by suitable control
Valve realizes the part filling of pump working chamber.It is powered by electromagnetic coil and realizes manipulation.The valve especially when electromagnetic coil powers off herein
The power of spring can largely cause the closing into valve without delay.Here, valve spring passes through valve components and adjustment plate
It acts on armature, armature is connect with valve follower.Therefore, valve follower is loaded by the pretightning force of valve spring.Valve spring is towards valve seat
Face loads valve follower.
Therefore, in the high-pressure pump as known to 10 2,010 027 745A1 of DE, fuel can be made by being maneuvered into valve
Pump working chamber is transported to from low-pressure chamber.Here, the manipulation into valve carries out during the suction stroke of pump piston.In pump piston
It is preferably what is closed to enter valve during conveying stroke.Be achieved in closing in no current state enters valve.Pass through valve spring
Correspondingly high initial tension of spring can realize high closing dynamic.But the defects of program, is, in order to make enter valve open and
It stays open, electromagnetic coil must be powered.Dynamic high initial tension of spring exactly is being closed for height, is being needed corresponding strong
Magnetic field, this brings high current and thus brings big power loss.Therefore, big control energy is generated in known scheme
Amount, because entering valve in entire sucting stage must stay open.
Invention content
The high-pressure pump of the present invention of the inlet valve of the present invention of feature with claim 1 and the feature with claim 8
The advantages of be that can preferably control the metering of fuel.Energy consumption can especially be reduced and thereby reduce required control energy.
The inlet valve and right to being provided in claim 1 can be realized by the measure provided in the dependent claims
It is required that the favourable improvement of the high-pressure pump provided in 8.
By pressure steps, valve closure body can be loaded in the direction of the opening.In the closing side being orientated against opening direction
Upwards, valve closure body can be loaded by armature by magnetic closing forces.Therefore, which is used to support the pass of inlet valve
It closes.It is preferred that closing movement is caused by the such degree of magnetic closing forces so that inlet valve enters throttling by not throttle.
Then largely cause closing in throttling by hydraulic coupling support closure or even at least.Hence it is advantageous to closing
No longer required magnetic closing forces at the end of process.Thus improve the manipulation of inlet valve.Particularly for closing power drain and must
The control energy needed reduces.
Advantageously, the seat diameter for being oriented to diameter and being less than seal receptacle for being oriented to valve closure body.The pressure as a result,
Ladder can be in the direction of the opening loaded according to prime discharge pressure with effective power.Thus it is corresponding in prime discharge pressure
It is big and at the same time the opening of inlet valve occurs in the case of pressure reduction in pump working chamber based on pressure proportional so that fuel
It is transported in pump working chamber by open seal receptacle.
Herein it is further advantageous that the valve closure body is connect by coupling bar (bibcock) with armature, the coupling bar is having
Have to be oriented in the pilot hole of diameter and be directed to, also, a valve chamber is formed between pilot hole and seal receptacle, in prime delivery pressure
Fuel under power can be channeled in the valve chamber, and armature is arranged in armature chamber, and the armature chamber in pilot hole by being directed to
Bibcock and valve chamber separate, also, the armature chamber is release for prime discharge pressure.Therefore, the fuel in valve chamber
Prime discharge pressure can advantageously cause effective power in the direction of the opening, still, with the pressure correlation in pump working chamber
, power in the closing direction is directed toward on the contrary with aforementioned power.However, during the suction stroke of the pump piston of high-pressure pump, pump
Pressure reduction in operating room so that opening force in the direction of the opening is formed in summation, which to convey in prime
Fuel under pressure can be flowed into pump working chamber.
Valve spring can be advantageously provided with, it is at least indirectly in the closing direction to the loading of valve closure body.Herein also
Advantageously, the valve spring be arranged in the armature chamber where armature and/or, the valve spring is by armature and/or bibcock
Valve closure body is loaded, which makes armature be connect with valve closure body.On the one hand the spring of closing limits the initial of inlet valve
Position.On the other hand by selection close spring spring constant and given pretightning force can generate in the closing direction with
Offset and thereby the spring force risen with opening stroke.This makes it possible to coordinate inlet valve.
It is also advantageous that being provided with control device, it during the shutoff stroke of valve closure body by making electromagnetic coil
It is powered to cause the electromagnetically-operated to armature, wherein, which makes electromagnetic coil be converted before seal receptacle completely closes
To no current.It reduce required manipulation energy.Thus the cooling requirement for electromagnetic coil is also reduced.It is also advantageous herein
It is that control device during the shutoff stroke of valve closure body by making electromagnetic coil be powered to manipulate valve closure body, until close
It seals and throttling is realized on seat.If realizing throttling on seal receptacle, further shutoff stroke can be purely mechanically by pumping work
Make the interior chamber pressure of the rising of room to close.
It therefore being capable of the advantageously (pressure drop in the trip in pump working chamber in the suction stroke of pump mounting assembly
It is low) by acting on the prime discharge pressure on the pressure steps valve closure body is manipulated in the direction of the opening.In addition, if
Valve closure body is made to be manipulated in the closing direction by such degree by the electromagnetically-operated to armature, so that being realized on seal receptacle
Throttling then (pressure rise in the trip in pump working chamber) can make valve closure body in the conveying stroke of pump mounting assembly
It is manipulated in the closing direction by the pressure in pump working chamber.
Description of the drawings
The present invention is explained in detail by attached drawing in the following description, corresponding element is provided with unification in the accompanying drawings
Reference numeral.Attached drawing is shown：
Fig. 1 one embodiment according to the invention, have inlet valve high-pressure pump partially schematic sectional view,
Fig. 2 is used to explain the curve graph of the high-pressure pump of one embodiment according to the invention and the functional mode of inlet valve,
Fig. 3 is used to explain another curve of the high-pressure pump of the embodiment according to the invention and the functional mode of inlet valve
Figure,
Fig. 4 is used to explain another curve of the high-pressure pump of the embodiment according to the invention and the functional mode of inlet valve
Figure.
Specific embodiment
Fig. 1 illustrates the high-pressure pump 1 according to one embodiment of the invention with partially schematic section.The high-pressure pump 1 especially may be used
To be configured to radial piston pump or tandem piston pump.The high-pressure pump 1 particularly suitable as petrolift for compressed air, from point
The fuel injection apparatus of the internal combustion engine of fire.High-pressure pump 1 has inlet valve 2.The inlet valve 2 is particularly suitable to be used in this high-pressure pump 1
In.But inlet valve 2 according to the invention is also applied for other application occasion in the case where accordingly adaptedly changing.
The high-pressure pump 1 and inlet valve 2 are preferably applied in the fuel injection apparatus with fuel distribution lath, the combustion
Diesel oil under material distribution lath storage high pressure.But it can also be controlled by inlet valve 2 and other suitable liquid is conveyed by high-pressure pump 1
Body, i.e., other liquid as fuel.
High-pressure pump 1 has cylinder head 3, forms the pump working chamber 4 of pump mounting assembly 5 wherein.Here, it is formed in cylinder head 3
Cylinder holes 6, pump piston 7 are directed in the cylinder holes.The gauge pump working chamber 4 in cylinder holes 6 of pump piston 7.In addition in unshowned shell
The drive shaft 8 with cam 9 is supported in body.In operation, drive shaft 8 rotates about axis 10 and rotates.Pass through cam 9 herein
The manipulation to pump piston 7 occurs, this is represented by double-head arrow 11.The manipulation can for example by being supported in roller boots rolling
Son carries out.
Inlet valve 2 has valve body 12, and seal receptacle 13 is formed on valve body.Seal receptacle 13 is in this embodiment circularly
It is configured with a diameter 14.It is provided with valve closure body 15 herein, its 13 collective effect of seal receptacle with valve body 12.
Valve body 12 is fixed on by closed screw on cylinder head 3.Sealing is formed between valve body 12 and cylinder head 3 herein,
So that pump working chamber 4 relative to environment it is high pressure resistant seal.
Inlet valve 2 has valve chamber 20, is conveyed by one or more holes 21,22 into the valve chamber in prime discharge pressure
Under fuel.Closure body 15 sticks on the seal receptacle 13 with seat diameter 14 under valve in off position in side.In addition, valve closes
Closure 15 connect with bibcock 23 or is integrally formed with the bibcock.Bibcock 23 is in the pilot hole for the matrix 25 that can be configured to magnetic core
It is directed in 24.Pilot hole 24 has herein is oriented to diameter 26, which is less than the seat diameter 14 of seal receptacle 13.Bibcock 23
It extend into armature chamber 27, which is release relative to the prime discharge pressure in valve chamber 20.Therefore pressure rank is formed
Ladder, the pressure steps are determined by the seat diameter 14 of seal receptacle 13 and the guiding diameter 26 of pilot hole 24.Therefore, it is defeated based on prime
Pressurization pressure generates the power being directed toward along the axis 29 of bibcock 23 to opening direction 28 on the pressure steps.
Inlet valve 2 also has armature 30, which connect with bibcock 23 and be arranged in armature chamber 27.In addition it is provided with
Electromagnetic coil 31, it can be powered by control device 32.When electromagnetic coil 31 is powered, which generates on armature 30
Magnetic force, thus valve closure body 15 in the closing direction 33 being directed toward against opening direction 28 by the seal receptacle 13 towards valve body 12
Direction loading.
It is additionally provided with valve spring 34 in this embodiment, it is by armature 30 and bibcock 23 to valve closure body 15 in closing side
It is loaded on 33.
Illustrate the configuration and functional mode of high-pressure pump 1 and inlet valve 2 also referring to Fig. 2,3 and 4 below.Fig. 2,3 and 4 distinguishes
One is shown for explaining the curve graph of the functional mode of high-pressure pump 1 and inlet valve 2.It marks on the horizontal scale in fig. 2 herein
Stroke of the valve closure body in opening direction 28, and mark on the vertical scale and the relevant flow of stroke.In figure 3 in abscissa
On mark stroke of the valve closure body 15 in opening direction 28, and mark on the vertical scale acted in closing direction 33 valve pass
Power on closure 15.It marks the time on the horizontal scale in Fig. 4, and marks the pressure in pump working chamber 4, valve pass on the vertical scale
The energization of stroke and electromagnetic coil 31 of the closure 15 in opening direction 28.
Curve 40 is illustratively shown in fig. 2, it represent between valve closure body 15 and seal receptacle 13 from valve chamber 20 to
Flow 40 in pump working chamber 4.When stroke is more than a value 41, then inlet valve 2 is in not throttling procedure, this leads in fig. 2
Region 42 is crossed to represent.Under value 41, inlet valve 2 is in throttling, this is represented by region 43.The flow 40 when stroke disappears
Also it disappears.
For explanation figure 3, from state 44s, in this state, inlet valve 2 is in no throttling band 42 and at this
Reach relatively large, the especially maximum stroke of valve closure body 15 in region.The spring of valve spring 34 is described by curve 45
The possible variation trend of power, the spring force are acted in closing direction 33 on valve closure body 15.Curve 45 and ordinate
Ordinate intersection point 46 illustrates the pretightning force not disappeared.The pretightning force of valve spring 44 can properly select herein.Curve 45 it is oblique
Rate can also be previously given by the spring constant of valve spring 34.In state 44, reset is applied by valve spring 34 substantially first
Power.If allow this point (such as in the conveying stroke of pump piston 7 with the pressure dependence in pump working chamber 4 in valve chamber 20
It is such case), then reset force of the valve closure body 15 based on valve spring 34 is turned off so that curve 47 is attached in curve 45 first
Near to continue, wherein curve continues direction and is represented by arrow 47.In region 48, lead to electromagnetic coil 31 by control device 32
Electricity.The precipitous rising of closing forces on valve closure body 15 is acted in closing direction 33 as a result, this is represented by arrow 49.By
This, applies maximum, force 50 on valve closure body 15.Here, less than value 41 so that inlet valve 2 is reached in throttling band 43.Herein
Stroke continues to reduce, this is represented by arrow 51.At the end of electromagnetic coil 31 is powered (this is represented by region 48), inlet valve
2 have been in throttling band 43.Therefore, can be applied in region 52 by the increased pressure of valve spring 34 and pump working chamber 4 into
The closing forces of one step.When stroke disappears (valve seat 13 is to close to inlet valve 2 in other words at this time), keep through curve 47 with indulging
Closing forces given by the ordinate intersection point 53 of coordinate.The closing forces are produced by the pretightning force of valve spring 34 and the pressure steps
It is raw.Therefore, ordinate intersection point 43 depends on prime discharge pressure (prime operating pressure).
Therefore relatively narrow region 48 is generated, electromagnetic coil 31 is needed to be powered in this region.Therefore, power drain is bright
It is aobvious to reduce.
It is shown in FIG. 4 time interval 48', 48 ", electromagnetic coil 31 is powered in these sections.Therefore, energization 54 passes through
Curve 54 with edge rise rapidly and decline represents.
Pressure in pump working chamber 4 is represented by curve 55.The pressure is respectively in time interval 48', 48 " rise in,
In, closing of the inlet valve 2 in throttling band 43 is supported by the pressure of the rising in pump working chamber 4 respectively.It is closed in inlet valve 2
After closing, pressure continues to rise, this is caused by the conveying stroke of pump piston 7.Curve 56 represents the variation of the stroke of valve closure body 15
Trend.In order to simplify the view, curve 54,55,56 since a common level, wherein, in the level initial value be not must
Must be zero.
Therefore, inlet valve 2 is configured to valve 2 outwardly opening, having pressure steps.If the interior room in pump working chamber 4
Pressure is less than the prime discharge pressure of 2 front of inlet valve, then valve closure body 15 is opened against valve spring 34.Pump working chamber 4 is filled
Note, until inlet valve 2 by the energization of electromagnetic coil 31 by electrically never throttle pulls out.It is further to close
Stroke is then purely mechanically realized by the interior chamber pressure of the rising of pump working chamber 4, because inlet valve 2 is in throttling.Therefore, have
Sharp ground obtains the extremely short manipulation time under small stroke situation of change, for activating the closing movement of inlet valve 2.
Therefore, depending on the configuration of inlet valve 2 or control device 32, region 48 can also include original state 44.
The closing of inlet valve 2 is then directly caused by the energization of electromagnetic coil 31.
The present invention is not limited to described embodiment.
Claims (9)
1. high-pressure pump (1), at least one cylinder head (3), with pump mounting assembly (5), which is included in cylinder head
(3) pump working chamber (4) formed in, the high-pressure pump also have at least one inlet valve (2), wherein, pass through the inlet valve (2)
Seal receptacle (13) can deliver fuel into pump working chamber (4), wherein, the inlet valve have and seal receptacle (13) jointly make
Valve closure body (15) simultaneously has armature (30) connect with valve closure body (15), Electromagnetically activatable, also, the armature
It (30) can be by such electromagnetically-operated so that the valve closure body (15) is being closed by the armature (30) by a magnetic closing forces
It closes on direction (33) and is loaded towards the seal receptacle (13),
It is characterized in that,
Equipped with armature chamber (27), it is connect with valve closure body (15) or extend into armature with its bibcock (23) being integrally formed
In room (27), which is release relative to the prime discharge pressure in valve chamber (20), to form pressure steps, by this
Pressure steps, valve closure body (15) can be loaded in opening direction (28),
Pressure reduction in the suction stroke of the pump mounting assembly (5) in pump working chamber (4) in the suction stroke, is led to
The prime discharge pressure acted on the pressure steps is crossed to make it possible to manipulate the valve closure body in opening direction (28)
(15)。
2. high-pressure pump as described in claim 1, which is characterized in that for the guiding diameter (26) being oriented to valve closure body (15)
Less than the seat diameter (14) of the seal receptacle (13).
3. high-pressure pump as claimed in claim 2, which is characterized in that the valve closure body (15) passes through bibcock (23) and armature
(30) connect, the bibcock (23) be oriented to diameter (26) pilot hole (24) in be directed to, pilot hole (24) with it is close
Valve chamber (20) is formed between envelope seat (13), the fuel under prime discharge pressure can be transported in the valve chamber, armature
(30) it is arranged in armature chamber (27), which is divided by the bibcock (23) being directed in pilot hole (24) with valve chamber (20)
It opens, also, the armature chamber (27) is release for the prime discharge pressure.
4. high-pressure pump as claimed any one in claims 1 to 3, which is characterized in that be provided with valve spring (34), the valve spring
The valve closure body (15) is loaded at least indirectly in closing direction (33).
5. high-pressure pump as claimed in claim 4, which is characterized in that the valve spring (34) is arranged in the rank where armature (30)
And/or, the valve spring (34) loads valve closure body (15) by armature (30) and/or bibcock (23) in iron room (27), should
Bibcock makes armature (30) be connect with valve closure body (15).
6. high-pressure pump as claimed any one in claims 1 to 3, which is characterized in that be provided with control device (32), the control
Device during the shutoff stroke of valve closure body (15) by making electromagnetic coil (31) be powered to cause the electromagnetism to armature (30)
It manipulates, wherein, the control device (32) makes electromagnetic coil (31) be transformed into no current before seal receptacle (13) completely closes.
7. high-pressure pump as claimed in claim 6, which is characterized in that the control device (32) passes through in valve closure body (15)
Electromagnetic coil (31) is made to be powered to manipulate the valve closure body (15) during shutoff stroke, until realizing section on seal receptacle (13)
Stream.
8. high-pressure pump as claimed any one in claims 1 to 3, which is characterized in that in the conveying of the pump mounting assembly (5)
Pressure rise in stroke in pump working chamber (4), in the conveying stroke, if made by the electromagnetically-operated to armature (30)
Valve closure body (15) is manipulated in closing direction (33) with this degree, is throttled so that being realized on seal receptacle (13), then institute
Valve closure body (15) is stated to be manipulated in closing direction (33) by the pressure in pump working chamber (4).
9. high-pressure pump as claimed any one in claims 1 to 3, which is characterized in that the high-pressure pump is for compressed air
, the radial piston pump or tandem piston pump of the fuel injection apparatus of the internal combustion engine of self-ignition.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102012213546.4A DE102012213546A1 (en) | 2012-08-01 | 2012-08-01 | High pressure pump for internal combustion engines |
| DE102012213546.4 | 2012-08-01 | ||
| 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 CN104508293A (en) | 2015-04-08 |
| CN104508293B true 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 (2)
| 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 |
| 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 |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102008018018A1 (en) * | 2008-04-09 | 2009-10-15 | Continental Automotive Gmbh | Pump for conveying a fluid |
| JP5401360B2 (en) * | 2010-02-26 | 2014-01-29 | 日立オートモティブシステムズ株式会社 | High pressure fuel supply pump |
| 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 CN CN201380040401.3A patent/CN104508293B/en not_active Expired - Fee Related
- 2013-07-24 EP EP13740010.7A patent/EP2880297B1/en not_active Not-in-force
- 2013-07-24 WO PCT/EP2013/065587 patent/WO2014019904A1/en active Application Filing
-
2014
- 2014-12-16 IN IN10748DEN2014 patent/IN2014DN10748A/en unknown
Patent Citations (2)
| 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 |
| 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 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104508293A (en) | 2015-04-08 |
| EP2880297B1 (en) | 2020-10-07 |
| EP2880297A1 (en) | 2015-06-10 |
| WO2014019904A1 (en) | 2014-02-06 |
| IN2014DN10748A (en) | 2015-09-04 |
| DE102012213546A1 (en) | 2014-02-06 |
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