EP2880297A1 - Hochdruckpumpe für brennkraftmaschinen - Google Patents
Hochdruckpumpe für brennkraftmaschinenInfo
- Publication number
- EP2880297A1 EP2880297A1 EP13740010.7A EP13740010A EP2880297A1 EP 2880297 A1 EP2880297 A1 EP 2880297A1 EP 13740010 A EP13740010 A EP 13740010A EP 2880297 A1 EP2880297 A1 EP 2880297A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- armature
- closing 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
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 8
- 238000007789 sealing Methods 0.000 claims abstract description 26
- 239000000446 fuel Substances 0.000 claims description 17
- 238000002347 injection Methods 0.000 claims description 4
- 239000007924 injection Substances 0.000 claims description 4
- 230000004913 activation Effects 0.000 abstract 1
- 238000010586 diagram Methods 0.000 description 4
- 230000001419 dependent effect Effects 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 230000036316 preload Effects 0.000 description 3
- 230000000630 rising effect Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005086 pumping 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
Definitions
- the invention relates to a suction valve for a high-pressure pump, which is used in particular for air-compressive, self-igniting internal combustion engines, and a high-pressure pump, in particular a radial or in-line piston pump.
- the high-pressure pump can also serve as a piston pump for conveying other suitable liquids.
- a high-pressure pump which serves in particular as a radial or in-line piston pump for fuel injection systems of air-compressing, self-igniting internal combustion engines.
- an inlet valve is provided, via which a metering of a guided into a pump working space fuel is possible. This can be done a full filling of the pump working space.
- a partial filling of the pump working space can be achieved by a suitable control of the inlet valve.
- the actuation takes place by energizing a magnetic coil.
- the solenoid is deenergized, the force of a valve spring can initiate a closing of the inlet valve largely without delay.
- the valve spring acts via a valve element and a shim on an anchor, which is connected to a valve lifter.
- the valve stem is biased by the bias of the valve spring.
- the valve spring acts on the valve stem against the
- the inlet valve is preferably closed.
- an intake valve is realized, which is closed in the de-energized state.
- a high closing dynamics can be achieved.
- this embodiment has the disadvantage that for opening and keeping open the Inlet valve solenoid coil must be energized. Especially at a high
- High-pressure pump according to the invention with the features of claim 8 have the advantage that an improved control for the metering of fuel is made possible. In particular, energy consumption and the drive energy thus required can be reduced.
- the measures listed in the dependent claims are advantageous
- Valve closing body acted upon by the magnetic closing force via the armature.
- the magnetic closing force therefore serves to support the closing of the suction valve.
- the closing movement is initiated so far by the magnetic closing force that the suction valve passes from a de-throttled state in the throttling.
- the throttling closing is then supported by the hydraulic forces or even at least largely conditional.
- the magnetic clamping force is therefore no longer needed in an advantageous manner at the end of the closing process. This improves the control of the suction valve.
- the magnetic closing force is therefore no longer needed in an advantageous manner at the end of the closing process. This improves the control of the suction valve.
- the magnetic closing force therefore serves to support the closing of the suction valve.
- the closing movement is initiated so far by the magnetic closing force that the suction valve passes from a de-throttled state in the throttling.
- the magnetic clamping force is therefore no longer needed in an advantageous manner at the end of the closing process. This improves the control of the suction valve.
- a guide diameter for guiding the valve closing body is smaller than a seat diameter of the sealing seat.
- the pressure stage can act on the valve closing body in the opening direction with an effective force as a function of the prefeed pressure.
- the pressure opening causes the suction valve to open, so that fuel is conducted into the pump working chamber via the opened sealing seat.
- the valve closing body is connected via a connecting bolt (valve pin) with the armature that the
- the prefeed pressure of the fuel in the valve chamber can advantageously bring about an effective force in the opening direction, which, however, is directed counter to a force dependent on the pressure in the pump working space in the closing direction.
- the pressure in the pump working space is reduced, so that in the sum of an opening force in the opening direction, which allows the inflow of fuel under the prefeed pressure in the pump working space.
- a valve spring can be provided, which acts on the valve closing body at least indirectly in the closing direction.
- the valve spring is arranged in an armature space in which the armature is arranged, and / or that the valve spring acts on the valve closing body by means of the armature and / or a valve pin which connects the armature to the valve closing body.
- the closing spring defines for a starting position of the suction valve.
- a control which causes the magnetic actuation of the armature by energizing a solenoid during a closing stroke of the valve closing body, wherein the controller deenergizes the solenoid before a complete closing of the sealing seat. This reduces the required drive energy. This also reduces the cooling requirement for the solenoid coil.
- the control actuates the valve closing body by energizing the solenoid during the closing stroke of the valve closing body, until a throttling is achieved at the sealing seat. When the restriction at the sealing seat is reached, then the further closing stroke can be closed purely mechanically by the increasing interior pressure of the pump working space.
- FIG. 1 shows a high-pressure pump with a suction valve in a partial, schematic sectional view according to an embodiment of the invention.
- Fig. 2 is a diagram for explaining the operation of the high-pressure pump and the suction valve according to the embodiment of the invention
- Fig. 3 is another diagram for explaining the operation of the high pressure pump and the suction valve according to the embodiment of the invention.
- Fig. 4 is another diagram for explaining the operation of the high pressure pump and the suction valve according to the embodiment of the invention.
- Fig. 1 shows a high-pressure pump 1 in an abstract, schematic
- High-pressure pump 1 can be designed in particular as a radial or in-line piston pump. Specifically, the high-pressure pump 1 is suitable as a fuel pump for
- the high-pressure pump 1 has a suction valve 2.
- the suction valve 2 is particularly suitable for use in such high-pressure pumps 1.
- the suction valve 2 according to the invention is suitable in a suitably adapted modification, however, also for others
- a preferred use of the high pressure pump 1 and the suction valve 2 is for a fuel injection system with a fuel rail, which stores diesel fuel under high pressure.
- suitable liquids including other liquids than fuel, controlled by the suction valve 2 and of the
- the high-pressure pump 1 has a cylinder head 3, in which a pump working space 4 of a pump assembly 5 is formed.
- a pump working space 4 of a pump assembly 5 is formed in the cylinder head 3 .
- Cylinder bore 6 configured in which a pump piston 7 is guided.
- the pump piston 7 bounded in the cylinder bore 6, the pump working space 4.
- a drive shaft 8 is mounted with a cam 9 in a housing, not shown.
- the drive shaft 8 rotates about its axis of rotation 10. This occurs via the cam 9 to an actuation of the pump piston 7, which is illustrated by the double arrow 1 1.
- the actuation can take place, for example, via a roller mounted in a roller shoe.
- the suction valve 2 has a valve seat body 12 on which a sealing seat 13 is configured.
- the sealing seat 13 is circular in this embodiment with a
- valve closing body 15 is provided which cooperates with the sealing seat 13 of the valve seat body 12.
- the valve seat body 12 is fixed to the cylinder head 3 via a plug screw.
- a seal between the valve seat body 12 and the cylinder head 3 is formed, so that the pump chamber 4 is sealed against the environment high pressure resistant.
- the suction valve 2 has a valve space 20 into which fuel is conveyed via one or more bores 21, 22 under a prefeed pressure.
- the valve closing body 15 is located on the one hand on the sealing seat 13 with the
- valve closing body 15 is connected to a valve pin 23 or designed in one piece with this.
- the valve pin 23 is in one
- Guide bore 24 of a body 25 which may be configured as a magnetic core out.
- the guide bore 24 in this case has a guide diameter 26 which is smaller than the seat diameter 14 of the sealing seat 13.
- An armature space 27, in which the valve pin 23 protrudes, is pressure-relieved against the prefeed pressure in the valve chamber 20. Thus, a pressure level is formed, the over the seat diameter 14 of the sealing seat 13 and the
- Guide diameter 26 of the guide bore 24 is determined. Due to the
- the suction valve 2 also has an armature 30, which is connected to the valve pin 23 and arranged in the armature space 27.
- a magnetic coil 31 is provided which can be energized by a controller 32.
- Magnetic coil 31 generates this a magnetic force on the armature 30, whereby the
- valve spring 34 acts on the valve closing body 15 via the armature 30 and the valve pin 23 in the closing direction 33.
- FIGS. 2, 3 and 4 each show a diagram for explaining the operation of the high pressure pump 1 and the suction valve 2
- the abscissa represents the stroke of the valve closing body in the opening direction 28, while the ordinate indicates the flow dependent on the stroke.
- the stroke of the valve closing body 15 in the opening direction 28 is plotted on the abscissa, while the forces acting on the valve closing body 15 in the closing direction 33 are plotted on the ordinate.
- the time is plotted on the abscissa, while at the ordinate, a pressure in the pump chamber 4, the stroke of the valve closing body 15 in the opening direction 28 and energization of the magnetic coil 31 are applied.
- a curve 40 is shown as an example, the flow 40 between the valve closing body 15 and the sealing seat 13 from the valve chamber 20 in the
- Fig. 3 To explain the Fig. 3 is assumed a state 44 in which the suction valve 2 is in the de-throttled region 42 and in which a comparatively large, in particular maximum, stroke of the valve closing body 15 is achieved.
- a curve 45 By a curve 45, a possible course of the spring force of the valve spring 34 is shown in the
- Closing direction 33 acts on the valve closing body 15. Ordinatenschnitttician 46 of the curve 45 with the ordinate indicates a non-vanishing bias.
- the Preload of the valve spring 44 can be suitably chosen here.
- the slope of the curve 45 can be preset via the spring constant of the valve spring 34.
- the restoring force is initially applied essentially by the valve spring 34. If the pressure conditions in the valve chamber 20 and in the pump working chamber 4 allow this, which is the case for example in a delivery stroke of the pump piston 7, then the valve closing body 15 closes due to the restoring force of the valve spring 34, so that a curve 47 first in the vicinity of the curve 45th is traversed, with the direction of the curve is indicated by the arrow 47.
- the magnetic coil 31 is energized by the controller 32. This increases the on the
- Valve closing body 15 acting in the closing direction 33 closing force sharply, which is illustrated by the arrow 49.
- Valve closing body 15 exerted.
- the value falls below 41, so that the suction valve 2 enters the throttled region 43.
- the stroke further decreases, which is illustrated by the arrow 51.
- the energization of the magnetic coil 31 ends, which is illustrated by the area 48, then the suction valve 2 is already within the throttled area 43.
- the further closing force can therefore be determined by the valve spring 34 and the rising pressure of the
- the curve 56 illustrates the course of the stroke of the valve closing body 15.
- the suction valve 2 is designed as an outwardly opening valve 2 with a pressure stage. Is the interior pressure in the pump working space 4 smaller than that
- the valve closing body 15 opens against the valve spring 34.
- the pump working chamber 4 is filled until the suction valve 2 is electrically pulled out by energizing the solenoid coil 31 from the de-throttled phase.
- the further closing stroke can then be carried out purely mechanically by the increasing interior pressure of the pump working chamber 4, since the suction valve 2 is in the throttling.
- the advantage thus results in a very short drive time at a small Hubdelta to activate the closing movement of the suction valve 2.
- the region 48 can thus also include the initial state 44. Closing the
- Suction valve 2 is then initiated immediately by energizing the solenoid coil 31.
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
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102012213546.4A DE102012213546A1 (de) | 2012-08-01 | 2012-08-01 | Hochdruckpumpe für Brennkraftmaschinen |
PCT/EP2013/065587 WO2014019904A1 (de) | 2012-08-01 | 2013-07-24 | Hochdruckpumpe für brennkraftmaschinen |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2880297A1 true EP2880297A1 (de) | 2015-06-10 |
EP2880297B1 EP2880297B1 (de) | 2020-10-07 |
Family
ID=48856630
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13740010.7A Active EP2880297B1 (de) | 2012-08-01 | 2013-07-24 | Hochdruckpumpe für brennkraftmaschinen |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP2880297B1 (de) |
CN (1) | CN104508293B (de) |
DE (1) | DE102012213546A1 (de) |
IN (1) | IN2014DN10748A (de) |
WO (1) | WO2014019904A1 (de) |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3818607B2 (ja) * | 1997-01-27 | 2006-09-06 | 株式会社小松製作所 | カム駆動式の電子制御ユニットインジェクタの制御装置及びその制御方法 |
DE102008018018A1 (de) * | 2008-04-09 | 2009-10-15 | Continental Automotive Gmbh | Pumpe zur Förderung eines Fluids |
EP2295774A1 (de) * | 2009-08-18 | 2011-03-16 | Delphi Technologies Holding S.à.r.l. | Verfahren und Vorrichtung zur Steuerung einer Common-Rail-Einspritzpumpe |
JP5401360B2 (ja) * | 2010-02-26 | 2014-01-29 | 日立オートモティブシステムズ株式会社 | 高圧燃料供給ポンプ |
DE102010027745A1 (de) | 2010-04-14 | 2011-10-20 | Robert Bosch Gmbh | Hochdruckpumpe |
DE102010039832A1 (de) * | 2010-08-26 | 2012-03-01 | Continental Automotive Gmbh | Verfahren und Vorrichtung zum Erkennen eines Erreichens eines Schließpunkts eines hydraulischen Ventils |
-
2012
- 2012-08-01 DE DE102012213546.4A patent/DE102012213546A1/de not_active Withdrawn
-
2013
- 2013-07-24 WO PCT/EP2013/065587 patent/WO2014019904A1/de active Application Filing
- 2013-07-24 CN CN201380040401.3A patent/CN104508293B/zh not_active Expired - Fee Related
- 2013-07-24 EP EP13740010.7A patent/EP2880297B1/de active Active
-
2014
- 2014-12-16 IN IN10748DEN2014 patent/IN2014DN10748A/en unknown
Non-Patent Citations (1)
Title |
---|
See references of WO2014019904A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE102012213546A1 (de) | 2014-02-06 |
CN104508293A (zh) | 2015-04-08 |
WO2014019904A1 (de) | 2014-02-06 |
CN104508293B (zh) | 2018-07-03 |
EP2880297B1 (de) | 2020-10-07 |
IN2014DN10748A (de) | 2015-09-04 |
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