CN102052221A - Flow control valve for metering fluid medium, particularly in fuel-high pressure pump - Google Patents
Flow control valve for metering fluid medium, particularly in fuel-high pressure pump Download PDFInfo
- Publication number
- CN102052221A CN102052221A CN2010105304503A CN201010530450A CN102052221A CN 102052221 A CN102052221 A CN 102052221A CN 2010105304503 A CN2010105304503 A CN 2010105304503A CN 201010530450 A CN201010530450 A CN 201010530450A CN 102052221 A CN102052221 A CN 102052221A
- Authority
- CN
- China
- Prior art keywords
- armature
- flow control
- valve
- control valve
- needle
- 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
- 239000012530 fluid Substances 0.000 title claims abstract description 7
- 239000000446 fuel Substances 0.000 claims description 16
- 230000009467 reduction Effects 0.000 claims description 4
- 230000002195 synergetic effect Effects 0.000 claims description 4
- 150000001875 compounds Chemical class 0.000 description 5
- 238000002485 combustion reaction Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000005284 excitation Effects 0.000 description 2
- 239000002828 fuel tank Substances 0.000 description 2
- 235000004240 Triticum spelta Nutrition 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000004907 flux Effects 0.000 description 1
- 239000003502 gasoline Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000010358 mechanical oscillation Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 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
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
- F02M37/0023—Valves in the fuel supply and return system
-
- 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
- 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
- F02M63/0021—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of mobile armatures
-
- 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
- F02M63/0021—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of mobile armatures
- F02M63/0022—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of mobile armatures the armature and the valve being allowed to move relatively to each other
-
- 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
- F02M63/0075—Stop members in valves, e.g. plates or disks limiting the movement of armature, valve or spring
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)
Abstract
The invention relates to a flow control valve for metering fluid medium, particularly in a fuel-high pressure pump (3). The flow control valve comprises a valve component which consists of a valve body (38), a valve needle (30) and an armature (20) capable of moving by means of an electromagnet (15). The valve needle can at least temporarily conduct loading on the valve body (38) in the opening direction of the valve needle, and can move between the closing position area and the opening position area. The movement of the armature is limited by a backstop (26) at least in the closing direction. The valve needle (30) comprises a slaving piece (32) which cooperates with the armature (20) in the closing direction. The backstop (26) is positioned, thereby the armature (20) reaches the backstop before the valve needle (30) arrives at the closing position area, and the valve needle (30) has a free path (55) relative to the armature (20). The free path is so large that the valve needle (30) can continue to move to the closing position area when the armature (20) reaches the backstop (26).
Description
Technical field
The present invention relates to a kind of be used for the meter fluid medium especially at the flow control valve (Mengensteuerventil) of high-pressure fuel pump.
Background technique
The fuel system that is used for internal-combustion engine is known on market, influences the fuel quantity of importing to high-pressure service pump by flow control valve in these fuel system.Such flow control valve is usually by operation electriomagnet and have for example compound body of the rigidity coupling of magnetic armature and needle.At this, the working stroke of magnetic armature is equivalent to the working stroke of needle.
In addition, with reference to the following discloses document: DE 102007034038A1, DE 102007028960A1, DE 102005022661A1, DE 102004061798A1, DE 2004016554A1, DE 10327411A1, DE 19834121A1, EP 1701031A1, EP 1471248A1 and EP 1296061A2.
Summary of the invention
Technical problem to be solved by this invention solves by flow control valve according to the present invention, and favourable expansion scheme provides below.This flow control valve has the valve element, this valve element comprises valve body, needle and can be by the armature of electromagnet motion, needle at least temporarily loads valve body and can move between closed position zone and open position zone opening on the direction, the motion of armature is limited by backstop on closing direction at least, wherein, needle is included on the closing direction and the synergistic moving part of taking of armature, backstop is located in this wise, make armature before needle arrives the closed position zone, arrive backstop, and make needle have free path with respect to armature, this free path is at least so big, makes that this needle can continue to move in the closed position zone when armature arrives backstop.In addition, in the important feature specification and accompanying drawing below of the present invention, wherein, these features may be not only individually but also with different combinations is important for the present invention, need not this is spelt out once more.
Flow control valve according to the present invention has the following advantages: can reduce armature travel, wherein, the load of armature, needle and backstop is reduced.Simultaneously, the quality of motion can be reduced, and makes electromagnet also can determine size more weakly.Reduced flow control valve price in the mill thus.In addition, because armature travel is reduced, the terminal velocity of armature also is reduced, and makes noise be reduced equally, and armature has terminal velocity on colliding backstop the time.
According to the present invention, armature and needle are realized as the element that separates, be that is to say that they do not constitute the compound body of rigidity.Replace the compound body that constitutes rigidity, armature and needle can relatively move in the axial direction, and wherein, armature and needle are loaded by spring and can intercouple by taking moving part on a direction (direction is moved in the suction of armature) at least.
Flow control valve has armature, and this armature can move axially between stationary holder and armature stop.In the original state of not energising, armature is pressed against on the stationary holder by armature spring.Needle is arranged in the axial bore of armature movably, and this needle is pressed against on the armature by valve spring by the dish (" taking moving part ") of fixedlying connected with it.Obtain an open position zone thus, wherein this needle can act on the valve body, at least temporarily valve body is lifted away from from valve seat.
If set out thus to armature energising, then armature is lifted away from and towards the armature stop motion from stationary holder, wherein armature in the pressure mode by the moving needle of dribbling.When armature arrival armature stop, needle may continue to move and temporarily be lifted away from from armature owing to its inertia and against the power that valve spring loads armature, to move in the closed position zone.This closed position zone comprises the residing All Ranges of needle when valve body is bearing on the valve seat of valve body.According to the present invention, armature stop is located in this wise, makes armature arrive armature stop before needle arrives the closed position zone.Therefore, needle has the so-called free travel with respect to armature, and needle can irrespectively continue to move on closing direction with this free travel and armature.
Needle does not have the speed that reduces at least in needle is not bearing in those motion stages on the armature.Therefore, avoided the pressure surge in the flow control valve and reduced the excitation of mechanical oscillation, the noise that also obtains thus reducing forms.In addition, the additional structure space that the present invention needs is little or do not need the additional structure space, and can advantageously be combined in the existing embodiment of flow control valve.
Propose in addition, needle is loaded opening on the direction by the spring that is supported on the housing section.The power of definition acts on the needle by this way, and the power that needle will define aspect that at it is delivered on armature and/or the valve body.Therefore, the behavior of flow control valve can be reproduced well.
A kind of configuration of flow control valve proposes, and spring performance is selected in this wise, make to be not less than limiting value as long as cross over the pressure reduction of described valve body, even if then during delivery phase armature be arranged in this valve body of open position and still be maintained in its closed position.Therefore, though according to the present invention needle can to the pass closed procedure of valve body begin exert an influence, keep after this valve closing, as long as the limiting value of pressure reduction is not exceeded.Therefore, weak relatively valve spring can be used, therefore also relatively little electromagnet can be used.
Opening when loading on the direction when armature is supported on spring on the housing section, the structure of flow control valve is simpler.This spring can protectively be placed in the dead slot of armature stop, make armature during by backstop this spring do not damaged by pressure.Also advantageously, the no current ground of opening of valve takes place.
Correspondingly propose, when armature was energized, this armature was implemented one stroke on closing direction for this reason.Then, armature can be inhaled and drive needle in the pressure mode, makes advantageously also to obtain above-mentioned effect in the closed procedure of the pass of flow control valve.
When the backstop that acts on closing direction of armature was pole core, the price of flow control valve reduced.Therefore, not only can save special backstop, and armature and pole core collide closely, thereby set up corresponding high magnetic flux.
The another kind of configuration of flow control valve proposes, and needle does not comprise with armature is opening the synergistic moving part of taking on the direction.Therefore, take moving part and only act on closing direction, that is to say, needle only can be by the armature mandatory guidance on closing direction.And opening on the direction, needle is loaded by valve spring and is driven by valve spring, if the position of armature allows all the time.
Description of drawings
Set forth illustrative embodiments of the present invention with reference to the accompanying drawings.Shown in the drawings:
Fig. 1 illustrates the sketch of the fuel system of internal-combustion engine;
Fig. 2 is illustrated in the sketch of the flow control valve in first running state with sectional view;
Fig. 3 is according to the flow control valve in second running state of Fig. 2;
Fig. 4 is according to the flow control valve in the 3rd running state of Fig. 2; With
Fig. 5 is according to the flow control valve in the 4th running state of Fig. 2;
In all figure, even if in different forms of implementation, also use identical reference character with amount for the element of functional equivalent.
Embodiment
Fig. 1 illustrates the fuel system 1 of internal-combustion engine with the view of simplifying very much.Act as a fuel and both can consider that gasoline also can consider diesel oil.Unspecified and high-pressure service pump 3 that be configured to reciprocating pump is connected with fuel tank 9 with low pressure line 7 by aspiration 4, pre-transfer pump 5 in the upstream.In the downstream, high-pressure storage 13 (" rail altogether ") is connected on the high-pressure service pump 3 by pressure duct 11.Flow control valve 14 with electromagnetic operating device 15 (hereinafter referred to as electromagnet 15) hydraulically is arranged between low pressure line 7 and the high-pressure service pump 3.Other element is not shown, for example the valve of high-pressure service pump 3 in Fig. 1.Obviously, flow control valve 14 can be constructed with the element of construction of high-pressure service pump 3.For example, can open the inlet valve of high-pressure service pump 3 in the pressure mode by flow control valve 14.
In service in fuel system 1, pre-transfer pump 5 is transported to fuel the low pressure line 7 from fuel tank 9.At this, flow control valve 14 determines that its mode is that this flow control valve keeps the inlet valve of high-pressure service pump 3 to open temporarily, forcibly from the fuel quantity of high-pressure service pump 3 to high-pressure storage 13 inputs during the current drainage stroke.
Four successively continuous mutually in time running statees of ensuing Fig. 2 to 5 expression flow control valve 14, these running statees are corresponding to the work cycle of high-pressure service pump 3 in so-called fully loaded supply.Fully loaded supply is interpreted as a kind of operation of flow control valve 14, and is in service to the maximum fuel quantity of high-pressure storage 13 meterings at this, that is to say that the inlet valve of high-pressure service pump 3 cuts out during whole delivery phase to a great extent.At this moment, these elements of flow control valve 14 are operated by electromagnetic ground and are effectively, on the meaning of control or adjusting the fuel quantity that measures are not had remarkable influence although these elements are current.
Fig. 2 and 3 is illustrated in the running state during the suction stage of high-pressure service pump 3, and Figure 4 and 5 characterize the feature of ensuing delivery phase.Between Fig. 3 and 4, realize the quick but continuous transition from the suction stage to the delivery phase in time.Describe the critical elements of flow control valve 14 below by Fig. 2, in ensuing Fig. 3 to 5, these critical elements are only repeated in for the scope of setting forth the working principle needs.
Fig. 2 only illustrates some elements important to the present invention in the schematic cross sectional view of flow control valve 14.These elements have the structure of radial symmetric basically.This flow control valve 14 is current to be the constituent element of the high-pressure service pump 3 that do not elaborate.As long as electromagnet is energising not, then can be pressed against on the stationary holder 24 by armature spring 22 by axially movable armature 20.These stationary holder 24 current baffle plate realizations by inserting.On the left side of figure, armature spring 22 enters into the dead slot 25 of armature stop 26, and this armature stop 26 is current also to be pole core 28.The axial bore that needle 30 passes armature 20 leads movably.Near (in figure left side) end section of needle 30, constitute the dish 32 of taking moving part and be arranged on regularly on the needle 30.Valve spring 34 is supported on the housing section 36 and is opening on the direction roof pressure dish 32 and roof pressure needle 30 thus to the right in the drawings, and shown in running position in also they are pressed against on the static armature 20.This needle 30 and armature 20 integral body belong to a valve element (not having reference character), and this valve element belongs to the inlet valve of high-pressure service pump 3 again.This needle 30 and armature 20 do not constitute fixing compound body.The valve disc 38 of expression valve body is arranged in the right side part of Fig. 2, and this valve disc is the part of valve element equally.This valve disc 38 can move axially between the valve seat 40 of case side and valve backstop 42.In the drawings, valve seat 40 is on valve disc 38 left sides, and valve backstop 42 is on valve disc 38 the right.The valve disc spring is not illustrated by related, and this valve disc spring is pressed against valve disc 38 on the valve seat 40 with smaller power.
In the drawings, valve zone 44 is positioned at valve seat 40 left sides, and the conveying chamber 46 of high-pressure service pump 3 is positioned at valve seat 40 the right.Valve zone 44 and conveying chamber 46 are filled fluid, promptly are filled fuel.Be in operation, during the intake stroke under the situation that inlet valve is opened, fuel is transported to the conveying chamber 46 from valve zone 44.Required for this reason precondition is that valve disc 38 is opened, and that is to say that valve disc must be lifted away from from its valve seat 40.
The position of valve disc 38 is subjected to following influence: the pressure reduction between valve zone 44 and the conveying chamber 46; The position of armature 20 and needle 30 and kinergety; Armature spring 22, valve spring 34, valve disc spring (not shown); With the flow of liquid in valve disc 38 zones.
During the suction stage of high-pressure service pump 3, flow control valve 14 is arranged in initial position in Fig. 2.During this suction stage, the pressure in the valve zone 44 is higher than the pressure in the conveying chamber 46.At this, valve disc 38 also is being compressed against on the valve backstop 42 under the situation of the assistance that does not have needle 30 owing to current pressure and flowing relation.That is to say that flow control valve 14 is opened.The armature travel that line segment 48 expresses possibility, the possible stroke of line segment 50 expression valve discs 38.Can find out that possible armature travel 48 is less than the possible stroke of valve disc 38.
Fig. 3 is illustrated in during the suction stage flow control valve 14 in the then state of Fig. 2.Electromagnet 15 is energized during this period, makes armature 20 quicken towards armature stop 26.At this, play the dish 32 of taking the moving part effect and thus this needle 30 driven forcibly.Just in time show such time point, strike on the armature stop 26 at this time point armature 20.At this moment, the dish 32 of needle 30 still is bearing on the armature 20.Can find out that needle 30 still stretches out above valve seat 40 with plussage 52.
In Fig. 2 and 3, needle 30 is arranged in the open position zone.
Fig. 4 is illustrated on the time flow control valve 14 in the state of Fig. 3 and then.Fig. 4 represents the early stage feature of delivery phase simultaneously.Because quick build-up pressure in conveying chamber 46, pressure dependence is put upside down, and makes valve disc 38 abut in during this period on the valve seat 40.Inlet valve also cuts out now.This armature 20 keeps backstop on armature stop 26, but the dish of needle 30 32 temporarily is lifted away from from armature 20 with free path 55 owing to the inertia of needle, that is to say needle 30 (in the drawings left) overshoot.Gap 54 between the right part of needle 30 and the valve disc 38 has illustrated this point equally.But such gap 54 is exhausted optional.Yet free path 55 is must be at least the same big with the plussage 52 of needle in Fig. 3.
Fig. 5 is illustrated in during the delivery phase in time the flow control valve 14 in the then state of Fig. 4.This solenoid valve 15 is no longer switched on and armature 20 turns back on the stationary holder 24 of armature by armature spring 22.Needle 30 abuts on the valve disc 38 at its place, end on the figure right side.Pressure in the conveying chamber 46 is still enough big, continues to be pressed in valve disc 38 on the valve seat 40 and keeps inlet valve thus or flow control valve 14 cuts out so that also overcome the power of valve spring 34.Arrow 56 has illustrated the high pressure on the valve disc 38 of acting in the conveying chamber.
In Figure 4 and 5, needle 30 is arranged in the closed position zone.By following the suction stage of delivery phase, the circulation of describing in Fig. 2 to 5 repeats and continues with Fig. 2.
Aspect plussage 52 and the gap 54 by relatively the finding out of Fig. 3 and 4, in this case, bring the maximum armature travel of supporting by line segment 48 (see figure 2) marks by the mistake of needle 30.This means that armature travel is with the stroke of corresponding amount less than the compound body of fixing (not the illustrating) be made up of armature 20 and needle 30 here.Therefore, especially reduced the load of armature 20, needle 30, armature stop 26 and stationary holder 24.The acoustic excitation of flow control valve 14 and the pressure surge of fluid can be littler.In case of necessity, electromagnet 15 also can design more weakly.But, by free path 55 provide needle 30 for the enough total kilometres of closing of inlet valve.
The mode of execution shown in Fig. 2 to 5 of flow control valve 14 has taking moving part or coiling 22 of only acting on closing direction, that is to say, needle 30 only can be by armature 20 mandatory guidances on closing direction.
Claims (7)
1. the flow control valve (14) that is used for the meter fluid medium, especially the flow control valve in high-pressure fuel pump (3), described flow control valve has the valve element, described valve element comprises valve body (38), needle (30) and can be by the armature (20) of electromagnet (15) motion, described needle at least temporarily loads described valve body (38) and can move between closed position zone and open position zone opening on the direction, the motion of described armature is limited by backstop (26) on closing direction at least, wherein, described needle (30) is included on the closing direction and the synergistic moving part (32) of taking of described armature (20), it is characterized in that, described backstop (26) is located in this wise, make described armature (20) before described needle (30) arrives described closed position zone, arrive described backstop, and make described needle (30) have free path (55) with respect to described armature (20), described free path is at least so big, makes that described needle (30) can continue to move in the described closed position zone when described armature (20) arrives described backstop (26).
2. according to the flow control valve (14) of claim 1, it is characterized in that described needle (30) is loaded opening on the direction by the spring that is supported on the housing section.
3. according to the flow control valve (14) of claim 2, it is characterized in that, the characteristic of described spring is selected in this wise, make to be not less than limiting value as long as cross over the pressure reduction of described valve body (38), even if then during delivery phase described armature (20) be arranged in valve body described in the open position (38) and still be maintained in its closed position.
4. according to the flow control valve (14) of claim 2, it is characterized in that the spring that described armature (20) is supported on the housing section loads opening on the direction.
5. according at least one flow control valve (14) in the above claim, it is characterized in that when described armature was energized, described armature (20) was implemented one stroke on closing direction.
6. according to each flow control valve (14) in the above claim, it is characterized in that the backstop that acts on (26) of described armature (20) is pole core (28) on closing direction.
7. according to each flow control valve (14) in the above claim, it is characterized in that described needle (30) does not comprise with described armature (20) is opening the synergistic moving part (32) of taking on the direction.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102009046088.8 | 2009-10-28 | ||
| DE102009046088.8A DE102009046088B4 (en) | 2009-10-28 | 2009-10-28 | Quantity control valve, in particular in a high-pressure fuel pump, for metering a fluid medium |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102052221A true CN102052221A (en) | 2011-05-11 |
| CN102052221B CN102052221B (en) | 2016-08-03 |
Family
ID=43738057
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201010530450.3A Expired - Fee Related CN102052221B (en) | 2009-10-28 | 2010-10-28 | The especially flow control valve in high-pressure fuel pump for metering fluid medium |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN102052221B (en) |
| DE (1) | DE102009046088B4 (en) |
| IT (1) | IT1401540B1 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105804907A (en) * | 2011-06-01 | 2016-07-27 | 日立汽车系统株式会社 | High-pressure fuel supply pump with electromagnetic suction valve |
| CN106401823A (en) * | 2015-07-27 | 2017-02-15 | 罗伯特·博世有限公司 | Valve for metering a fluid |
| CN107869399A (en) * | 2016-09-27 | 2018-04-03 | 罗伯特·博世有限公司 | The method for controlling the valve that can be switched, the especially injection valve of the internal combustion engine of motor vehicle |
| CN110030131A (en) * | 2017-12-12 | 2019-07-19 | 罗伯特·博世有限公司 | For measuring the valve of fluid |
| CN110678642A (en) * | 2017-05-31 | 2020-01-10 | 日立汽车系统株式会社 | High-pressure fuel supply pump |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3187725B1 (en) * | 2014-08-28 | 2019-06-05 | Hitachi Automotive Systems, Ltd. | High-pressure fuel supply pump |
| DE102019210906A1 (en) * | 2019-07-23 | 2021-01-28 | Robert Bosch Gmbh | Valve for metering a fluid |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1119885A (en) * | 1993-03-26 | 1996-04-03 | 美国西门子汽车公司 | Impact dampened armature and needle valve assembly |
| EP1471248A1 (en) * | 1999-02-09 | 2004-10-27 | Hitachi, Ltd. | High pressure fuel supply pump for internal combustion engine |
| US20040223856A1 (en) * | 2003-05-08 | 2004-11-11 | Robert Bosch Gmbh | Fuel supply pump, in particular a high-pressure fuel pump for an internal combustion engine |
| EP1701031A1 (en) * | 2005-03-11 | 2006-09-13 | Hitachi, Ltd. | An electromagnetic drive mechanism of a high-pressure fuel supply pump |
| DE102007028960A1 (en) * | 2007-06-22 | 2008-12-24 | Robert Bosch Gmbh | High-pressure pump for fuel system of internal combustion engine, has intake valve device, which is brought by actuation device to certain position or held in certain position |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19834121A1 (en) | 1998-07-29 | 2000-02-03 | Bosch Gmbh Robert | Fuel supply system of an internal combustion engine |
| EP1296061A3 (en) | 2001-09-21 | 2005-03-16 | Hitachi, Ltd. | High pressure fuel pump |
| DE10327411B4 (en) | 2002-10-15 | 2015-12-17 | Robert Bosch Gmbh | Pressure relief valve and fuel system with such a pressure relief valve |
| DE102004016554B4 (en) | 2004-04-03 | 2008-09-25 | Robert Bosch Gmbh | Method and device for controlling a solenoid valve |
| DE102004061798B4 (en) | 2004-12-22 | 2013-06-06 | Robert Bosch Gmbh | Electromagnetic valve, in particular for a fuel injection system of a motor vehicle |
| DE102005022661A1 (en) | 2005-05-17 | 2007-02-15 | Robert Bosch Gmbh | Fluid pump e.g. fuel-high pressure pump, for use in fuel system of internal combustion engine, has volume control valve that includes valve mechanism arranged parallel to another valve mechanism in fluidic manner |
| DE102007034038A1 (en) | 2007-07-20 | 2009-01-22 | Robert Bosch Gmbh | High-pressure pump for a fuel system of an internal combustion engine |
| DE102017211361A1 (en) | 2017-07-04 | 2019-01-10 | Robert Bosch Gmbh | Valve device for a high-pressure fuel pump |
-
2009
- 2009-10-28 DE DE102009046088.8A patent/DE102009046088B4/en not_active Expired - Fee Related
-
2010
- 2010-10-22 IT ITMI2010A001938A patent/IT1401540B1/en active
- 2010-10-28 CN CN201010530450.3A patent/CN102052221B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1119885A (en) * | 1993-03-26 | 1996-04-03 | 美国西门子汽车公司 | Impact dampened armature and needle valve assembly |
| EP1471248A1 (en) * | 1999-02-09 | 2004-10-27 | Hitachi, Ltd. | High pressure fuel supply pump for internal combustion engine |
| US20040223856A1 (en) * | 2003-05-08 | 2004-11-11 | Robert Bosch Gmbh | Fuel supply pump, in particular a high-pressure fuel pump for an internal combustion engine |
| EP1701031A1 (en) * | 2005-03-11 | 2006-09-13 | Hitachi, Ltd. | An electromagnetic drive mechanism of a high-pressure fuel supply pump |
| DE102007028960A1 (en) * | 2007-06-22 | 2008-12-24 | Robert Bosch Gmbh | High-pressure pump for fuel system of internal combustion engine, has intake valve device, which is brought by actuation device to certain position or held in certain position |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105804907A (en) * | 2011-06-01 | 2016-07-27 | 日立汽车系统株式会社 | High-pressure fuel supply pump with electromagnetic suction valve |
| CN105840374A (en) * | 2011-06-01 | 2016-08-10 | 日立汽车系统株式会社 | High-pressure fuel supply pump with electromagnetic suction valve |
| CN105840374B (en) * | 2011-06-01 | 2018-10-26 | 日立汽车系统株式会社 | Has the high-pressure fuel feed pump of electromagnetic suction valve |
| CN106401823A (en) * | 2015-07-27 | 2017-02-15 | 罗伯特·博世有限公司 | Valve for metering a fluid |
| CN106401823B (en) * | 2015-07-27 | 2020-05-22 | 罗伯特·博世有限公司 | Valve for metering a fluid |
| CN107869399A (en) * | 2016-09-27 | 2018-04-03 | 罗伯特·博世有限公司 | The method for controlling the valve that can be switched, the especially injection valve of the internal combustion engine of motor vehicle |
| CN110678642A (en) * | 2017-05-31 | 2020-01-10 | 日立汽车系统株式会社 | High-pressure fuel supply pump |
| CN110678642B (en) * | 2017-05-31 | 2022-03-01 | 日立安斯泰莫株式会社 | High-pressure fuel supply pump |
| CN110030131A (en) * | 2017-12-12 | 2019-07-19 | 罗伯特·博世有限公司 | For measuring the valve of fluid |
| CN110030131B (en) * | 2017-12-12 | 2023-03-24 | 罗伯特·博世有限公司 | Valve for metering a fluid |
Also Published As
| Publication number | Publication date |
|---|---|
| IT1401540B1 (en) | 2013-07-26 |
| DE102009046088A1 (en) | 2011-05-05 |
| DE102009046088B4 (en) | 2021-07-29 |
| CN102052221B (en) | 2016-08-03 |
| ITMI20101938A1 (en) | 2011-04-29 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102052221A (en) | Flow control valve for metering fluid medium, particularly in fuel-high pressure pump | |
| JP5052656B2 (en) | High pressure fuel supply pump and fuel supply system | |
| US20100206252A1 (en) | High-pressure pump for a fuel system of an internal combustion engine | |
| US9383028B2 (en) | Valve | |
| CN106795846A (en) | High-pressure fuel feed pump | |
| CN102472220B (en) | Pump unit | |
| CN104520566B (en) | Method for activating a switching element of a valve device | |
| US6481396B2 (en) | Electromagnetic actuator for operating a gas exchange valve of an internal combustion engine | |
| US9382885B2 (en) | Fuel injection valve for an internal combustion engine | |
| JP2010174849A (en) | Solenoid valve and fuel injection valve | |
| JP6957494B2 (en) | Magnetically directly controlled intake valve for fuel pump | |
| US10088069B2 (en) | Electromagnetically actuated valve | |
| CN108368805B (en) | Valve assembly for an injection valve and injection valve | |
| Matsumoto et al. | 4 th Generation Diesel Common Rail System: Realizing Ideal Structure Function for Diesel Engine | |
| CN102197213A (en) | High-pressure fuel pump for an internal combustion engine | |
| CN103635680B (en) | Method and apparatus for running automotive fuel conveying equipment | |
| CN108431398B (en) | Method for controlling high-pressure fuel supply pump and high-pressure fuel supply pump using same | |
| US20090320797A1 (en) | Electromagnetic proportional control valve for flow rate control and fuel supply pump | |
| JP6043865B2 (en) | High pressure fuel supply pump | |
| CN103649506A (en) | Method for operating a fuel delivery device | |
| US7063054B2 (en) | Valve driving device of an internal combustion engine | |
| US10514105B2 (en) | Multi-way valve as well as actuator comprising such a multi-way valve | |
| CN110678642B (en) | High-pressure fuel supply pump | |
| CN101446247B (en) | Fuel high-pressure pump for fuel system of internal-combustion engine | |
| CN109312703A (en) | It loads the part of single-piston petrolift |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| 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: 20160803 Termination date: 20211028 |