EP2628938B1 - Fuel injector valve - Google Patents
Fuel injector valve Download PDFInfo
- Publication number
- EP2628938B1 EP2628938B1 EP20130152149 EP13152149A EP2628938B1 EP 2628938 B1 EP2628938 B1 EP 2628938B1 EP 20130152149 EP20130152149 EP 20130152149 EP 13152149 A EP13152149 A EP 13152149A EP 2628938 B1 EP2628938 B1 EP 2628938B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- control
- control chamber
- chamber part
- throttle
- control body
- 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.)
- Not-in-force
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Classifications
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- 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
- F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
- F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
- F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
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- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
- F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
- F02M2200/708—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with hydraulic chambers formed by a movable sleeve
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- 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
- F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
- F02M2547/001—Control chambers formed by movable sleeves
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- 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
- F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
- F02M2547/008—Means for influencing the flow rate out of or into a control chamber, e.g. depending on the position of the needle
Definitions
- the invention relates to a fuel injection valve, in particular an injector for fuel injection systems of internal combustion engines. Specifically, the invention relates to the field of injectors for fuel injection systems of air compressing, self-igniting internal combustion engines.
- a nozzle module in which a nozzle needle cooperating with an injection nozzle is guided axially movable, to which a valve control chamber adjoins, which is connected via a inlet throttle having inlet channel with a high-pressure chamber.
- a valve control module is provided with a valve closing member which is arranged in a valve chamber which is connected via a flow restrictor having a drain passage with the valve control chamber.
- a bypass channel is provided in the known injection arrangement. In one injection operation, a valve lift of the valve closing member is 100%, so that the valve closing member rests against a second valve seat. This correlates a so-called control amount, which is discharged via the drainage channel and the valve chamber and which triggers a stroke of the nozzle needle.
- the from the DE 101 39 623 A1 known injection assembly has the disadvantage that at each actuation of the nozzle needle fuel is separated from the high pressure region in the low pressure region.
- the amount of tax consumed by each control process flows, for example via a low pressure return in a tank of a motor vehicle and must ultimately be returned through a high-pressure pump again.
- the extracted from the control room control amount thus contributes to the energy consumption of the entire fuel injection system. Therefore, it is expedient to reduce this control amount as possible, but without affecting the injection behavior by influencing the control process.
- a fuel injection valve which has a limited by the end face of a nozzle needle control chamber.
- a movable flow plate is arranged, which closes the inlet bore in the control room in certain operating conditions.
- the fuel injection valve according to the invention with the features of claim 1 has the advantage that an improved design is made possible, in particular, a control amount for driving the nozzle needle is reduced.
- the efficiency of the fuel injector can be improved, thus optimizing the overall efficiency of the particular fuel injection system. This reduces energy consumption. In addition, a resulting heat loss, especially in the area of the return can be reduced. This reduces the thermal load on the fuel injector and the other components of the fuel injection system.
- the control body locks in the shut-off position at least a direct connection between the outlet throttle and the inlet throttle over the first control chamber part. During actuation of the nozzle needle is thus avoided that under high pressure fuel flows over the inlet throttle in the first control chamber part and is immediately separated from the first control chamber part via the outlet throttle to low pressure.
- the control body blocks at least one direct connection between the outlet throttle and the inlet throttle via the first control chamber part, so that in any case the direct connection via the first control chamber part is blocked.
- an indirect connection may still exist here, in particular via a filling throttle and the second control chamber part.
- control body has a second end face which is remote from the first end face of the control body and that the second end face defines a fuel space in which the nozzle needle is arranged.
- the fuel chamber in which the nozzle needle is arranged, is in operation under high pressure fuel.
- This pressure acts on the second end face of the control body, so that a force acts on the control body.
- This force counteracts a force that is due to the pressure of the fuel in the control chamber, in particular in the first control chamber part.
- the control body in particular the size of second end face, thus the actuation process can be tuned. In this case, further forces, in particular a bias of a valve spring, act.
- control body has at its first end face a projection which, in the shut-off position, blocks at least the direct connection between the outlet throttle and the inlet throttle via the first control chamber part.
- the projection of the control body in the shut-off position separates an inner region of the first control chamber part from an outer region of the first control chamber part, which surrounds the inner region in an annular manner, that the outlet throttle opens into the inner region of the first control chamber part and that the inlet throttle opens into the outer region of the first control chamber part.
- the high pressure in the outer region acts on the first end face of the control body, which delimits the first control chamber part.
- the inner region of the first control chamber part is connected via the outlet throttle with the low pressure, so that a pressure reduction in the inner region or a stroke of the nozzle needle is made possible.
- the volume of the control chamber, in particular of the second control chamber part decreases because the volume of the second control chamber part decreases in the blind hole of the control body by the stroke of the nozzle needle.
- an annular shut-off seat is configured on the projection and that a diameter of the annular shut-off seat and a needle diameter of the nozzle needle are predetermined such that a quotient with a dividend equal to the diameter of the annular shut-off seat and a divisor, which is equal to the needle diameter, is in a range of about 0.8 to about 1.5.
- connection between the first control chamber part and the second control chamber part is configured as a throttled connection
- the control body has a throttled connection bore, which forms the throttled connection between the first control chamber part and the second control chamber part, and that the throttled connection bore of the control body opens into the inner region of the first control chamber part. Since the hydraulic connection between the first control chamber part and the second control chamber part is configured as a throttled connection, the release of the direct connection between the outlet throttle and the inlet throttle via the first control chamber part can be assisted by additional hydraulic forces on the control body. Specifically, the release of the Absperrsitzes be supported on the projection of the control body by these additional hydraulic forces on the control pot.
- control body is arranged on a longitudinal axis of the nozzle needle.
- throttled connection bore is arranged on the longitudinal axis of the nozzle needle.
- outlet throttle is arranged on the longitudinal axis of the nozzle needle.
- the inlet throttle opens into the outer region of the first control chamber part, and that the control body has a Mountaindrossel, which opens on the one hand in the outer region of the first control chamber part and the other opens into the second control chamber part.
- the filling throttle can be configured via a throttle bore or a similar hydraulic connection.
- a control sleeve is provided, that the control body is guided in a guide bore of the control sleeve, that the guide bore has a step, that the control body has a paragraph and that the shoulder of the control body to limit a displacement of the control body with the step the guide bore of the control sleeve cooperates.
- the first end face of the control body faces one side of a throttle plate, that the control body has a projection that on the
- Projection is designed a shut-off seat, that the Absperrsitz the projection in the shut-off position of the control body cooperates with the side of the throttle plate to lock at least the direct connection between the outlet throttle and the inlet throttle over the first control chamber part that between the first end face of the control body and the Side of the throttle plate, a spring element is arranged and that the spring element is biased in the shut-off position of the control body.
- the spring element may be formed for example by a leaf spring.
- Fig. 1 shows a first embodiment of a fuel injection valve 1 of the invention in a schematic, partial sectional view.
- the fuel injection valve 1 can serve in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines.
- a preferred use of the fuel injection valve 1 is for a fuel injection system with a common rail, the diesel fuel under high pressure leads to a plurality of fuel injection valves 1.
- the fuel injection valve 1 according to the invention is also suitable for other applications.
- the fuel injection valve 1 has a housing 2 and a throttle plate 3, which is suitably inserted into the housing 2.
- a fuel space 4 configured in which a nozzle needle 5 is arranged.
- the fuel injection valve 1 has a control valve 6 which can be actuated via an actuator 7, as illustrated by a double arrow 8.
- the actuator 7 may be configured, for example, as a magnetic actuator 7 or as a piezoelectric actuator 7.
- a high pressure line 9 is guided.
- the high-pressure line 9 is supplied under high-pressure fuel, which is taken for example from a common rail.
- the throttle plate 3 has a bore 10, via which the high-pressure fuel from the high-pressure line 9 is guided into the fuel chamber 4.
- the throttle plate 3 also has an outlet throttle 11 and an inlet throttle 12.
- the inlet throttle 12 branches off from the high-pressure line 9.
- the outlet throttle 11 leads to the control valve 6.
- the fuel injection valve 1 also has a control sleeve 15, on which a guide bore 16 is configured.
- the guide bore 16 is configured in this embodiment as a cylindrical guide bore 16.
- a control body 17 is guided along a longitudinal axis 18.
- the control sleeve 15 has a blind hole 19.
- One end 20 of the nozzle needle 5 is guided in the blind hole 19 along the longitudinal axis 18.
- the control body 17 has a first end face 21 and a second end face 22, which are remote from each other.
- the control body 17 has at the first end face 21 a projection 23 which is designed as an annular projection 23.
- an annular Absperrsitz 24 is configured, which is configured in this embodiment as an annular, in particular circular, Absperrsitz 24.
- the projection 23 divides the first end face 21 of the control body 17 into an outer surface 25 and an inner surface 26.
- the outer surface 25 is configured as an annular surface 25.
- the inner surface 26 is configured as a circular surface 26.
- the fuel injection valve 1 has a control chamber 30.
- the control room 30 comprises a first control room part 31 and a second control room part 32.
- the projection 23 of the control body 17 separates an outer portion 33 of the first control chamber part 31 of a Inner region 34 of the first control chamber part 31.
- the outer region 33 of the first control chamber part 31 is in this case between the outer surface 25 of the first end 21 of the control body 17 and a side 35 of the throttle plate 3.
- the inner region 34 of the first control chamber part 31 is located between The first control chamber part 31 is bounded by the first end face 21 of the control body 17, the side 35 of the throttle plate 3 and the guide bore 16.
- the second control chamber part 32 is bounded by an end face 36 of the nozzle needle 5 and the blind hole 19.
- the second control chamber part 32 is in this case between the end face 36 of the nozzle needle 5 and a surface 37 of the control body 17th
- the first end face 21 of the control body 17 limits the first control chamber part 31 of the control chamber 30.
- the end face 36 of the nozzle needle 5 limits the second control chamber part 32 of the control chamber 30 in the blind bore 19.
- the first control chamber part 31 is connected to the second control chamber part 32 via a connecting bore 38 connected.
- the connecting bore 38 is designed in this embodiment as unthrottled connecting bore 38.
- the connecting bore 38 can also be configured as a throttled connecting bore 38, as can be seen from the Fig. 3 is described.
- the outlet throttle 11 and the inlet throttle 12 open into the first control chamber part 31.
- the outlet throttle 11 opens into the inner region 34, while the inlet throttle 12 opens into the outer region 33.
- a direct connection between the outlet throttle 11 and the inlet throttle 12 is thus blocked via the first control chamber part 31.
- Fig. 2 shows a diagram for explaining the operation of a fuel injection valve according to a possible embodiment of the invention.
- the time t is plotted on the abscissa of the diagram.
- the valve lift 40 a needle lift 41 and a flow 42 through the inlet throttle 12 shown in the form of exemplary curves.
- the needle stroke 41 illustrates the opening and closing movement of the nozzle needle 5.
- the flow 42 through the inlet throttle 12 illustrates that from the high pressure line 9 via the inlet throttle 12 in the outer region 33 of the first control chamber part 31 and thus nachfdusden in the first control chamber part 31 fuel.
- the area under the curve 42 here is a measure of the flowing, under high pressure fuel quantity.
- the sequence of an operation is shown as an example.
- the fuel injection valve 1 In operation of the fuel injection valve 1 is located in the fuel chamber 4 under high pressure fuel.
- the pressure of the fuel in the fuel chamber 4 acts on the control body 17 via the second end face 22 of the control body 17. Furthermore, there is also in the control chamber 30 under high pressure fuel.
- the pressure of the fuel acts in the region of the first control chamber part 31 on the first end face 21 of the control body 17. This is a partial compensation, since the pressure in the second control chamber part 32 acts in the opposite direction on the surface 37. It should be noted that in the initial position of the control body 17 is at a sufficient distance from the side 35 of the throttle plate 3, so that the annular Absperrsitz 24 is open on the projection 23 and the inner portion 34 and the outer portion 33 of the first control chamber portion 31 not separated from each other, but are interconnected.
- the actuator 7 actuates the control valve 6.
- the outlet throttle 11 is released and fuel can flow out of the control chamber 30 to the low pressure.
- the pressure in the control room 30 drops slightly.
- the control body 17 moves in a direction 43. Because at the second end face 22 of the control body 17 continues to be high pressure of the fuel in the fuel chamber 4 at.
- the reduced pressure in the control chamber 30 also reduces the acting on the end face 36 of the nozzle needle 5 pressurization. As a result, the nozzle needle 5 also moves in the direction 43.
- control sleeve 15 strikes with its projection 23 on the side 35 of the throttle plate 3, so that the outer region 33 of the first control chamber part 31 is separated from the inner region 34 of the first control chamber part 31 becomes. A subsequent flow of fuel from the high pressure line 9 via the inlet throttle 12 in the inner region 34 of the control chamber 30 is thus prevented. The effluent via the outlet throttle 11 fuel thus causes a rapid opening of the nozzle needle. 5
- control body 17 quickly reaches its shut-off position, so that during the opening movement of the nozzle needle 5, that is, between the time t2 and the time t3 no flow of fuel through the inlet throttle 12 or such a flow is at least negligible, as is especially in the basis of the Fig. 3 described embodiment is the case.
- a vote is possible by the connecting hole 38 is performed as a throttled connection bore 38.
- control body 17 can be adjusted even faster compared to the opening movement of the nozzle needle 5 in the shut-off position.
- the blocking of the inlet throttle 12 is achieved because the control body 17 moves rapidly after opening the outlet throttle 11 in the direction 43.
- the cause of the movement of the control body 17 is in the pressure reduction in the first control chamber part 31 and in the second control chamber part 32 relative to the high pressure in the fuel chamber 4 when the control valve 6 is opened.
- a resultant force is established, which adjusts the control body 17 in the direction 43 against the side 35 of the throttle plate 3.
- the control body 17 remains in the shut-off position as long as the pressure in the control chamber 30 is less than the high pressure in the fuel chamber 4.
- the control chamber pressure can be specified, from which the sealing seat on the annular Absperrsitz 24 of the control body 17 is released.
- Advantageous values for the diameter 50 of the annular Absperrsitzes 24 are 0.8 times to 1.5 times the needle diameter 51.
- the diameter 50 of the annular Absperrsitzes 24 and the needle diameter 51 of the nozzle needle 5 are thus preferably set so that a Quotient with a dividend equal to the diameter 50 of the annular lock seat 24 and a divisor equal to the needle diameter 51, in a range of about 0.8 to about 1.5.
- the nozzle needle 5 is actuated by hydraulic forces and optionally spring forces against the direction 43, wherein the control body 17 is mitver Victoria.
- the sealing seat on the annular shut-off seat 24 is released and the closing of the nozzle needle 5 can be done very quickly by flowing high pressure fuel through the inlet throttle 12. If the connection bore 38 is designed as a throttled connection bore, then the release of the shut-off seat 24 can be assisted by additional hydraulic forces on the control body 17.
- the control body 17 is freely movable or displaceably mounted in the guide bore 16.
- the control body 17 is configured in this embodiment as a cup-shaped control body 17, that is, as a control pot 17.
- Fig. 3 shows a fuel injection valve 1 in a partial, schematic sectional view according to a second embodiment.
- the connecting bore 38 which connects the first control chamber part 31 to the second control chamber part 32, is configured as a throttled connecting bore 38.
- the control body 17 has a Golfdrossel 55, which opens on the one hand in the outer region 33 of the first control chamber part 31 and on the other hand in the second control chamber part 32.
- the guide bore 16 is configured in this embodiment as a stepped guide bore 16.
- the guide bore 16 in this case has a step 56.
- the control body 17 has a step 56 associated paragraph 57.
- the paragraph 57 of the control body 17 acts to limit an adjustment 58 of the control body 17 with the step 56 of the guide bore 16 together. Upon opening of the control valve 6, the control body 17 thus reaches the shut-off position after a maximum displacement 58.
- a spring element 59 is provided, which is arranged between the first end face 21 of the control body 17 and the side 35 of the throttle plate 3.
- the spring element 59 which may be configured as a plate spring 59, a defined starting position of the control body 17 is predetermined.
- the control body 17 when releasing the outlet throttle 11 via the control valve 6 can be ensured.
- the reaction time is limited by the predetermined maximum adjustment path 58.
- the spring element 59 can act on the control body 17 in the direction 43 with a bias.
- control body 17 locks in the shut-off a direct connection between the outer region 33 and the inner region 34 of the first control chamber part 31.
- an indirect connection is given.
- the filling throttle 55 and the throttled connecting bore 38 are, however, connected in series, so that the possibly possible flow 42 through the inlet throttle 12 when opening the nozzle needle 5 is negligible. Therefore, also in this embodiment, a situation arises, as for example, based on the in Fig. 2 illustrated diagram is illustrated.
- the inlet throttle 12 can be closed at least temporarily with the control valve 6 open, or at least a reduction of the supplied high-pressure quantity can be achieved.
- the control valve 6 is closed, the inlet throttle 12 is released again.
- the control amount can be significantly reduced.
- the temperature in the return can be reduced.
- the throttle effect of the outlet throttle 11 and the throttling effect of the inlet throttle 12 can be freely selected within certain limits. As a result, a flexible specification of the opening and closing speed of the nozzle needle 5 is possible.
- the efficiency of the fuel injection valve 1 can be improved because the flow rate 42 through the inlet throttle 12 is limited in time and thus the control amount is reduced. As a result, lower carbon dioxide emissions of a motor vehicle or the like can be achieved.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fuel-Injection Apparatus (AREA)
Description
Die Erfindung betrifft ein Brennstoffeinspritzventil, insbesondere einen Injektor für Brennstoffeinspritzanlagen von Brennkraftmaschinen. Speziell betrifft die Erfindung das Gebiet der Injektoren für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen.The invention relates to a fuel injection valve, in particular an injector for fuel injection systems of internal combustion engines. Specifically, the invention relates to the field of injectors for fuel injection systems of air compressing, self-igniting internal combustion engines.
Aus der
Die aus der
Aus der
Das erfindungsgemäße Brennstoffeinspritzventil mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass eine verbesserte Ausgestaltung ermöglicht ist, bei der insbesondere eine Steuermenge zur Ansteuerung der Düsennadel reduziert wird.The fuel injection valve according to the invention with the features of claim 1 has the advantage that an improved design is made possible, in particular, a control amount for driving the nozzle needle is reduced.
Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen des im Anspruch 1 angegebenen Brennstoffeinspritzventils möglich.The measures listed in the dependent claims advantageous developments of the fuel injection valve specified in claim 1 are possible.
Durch die Reduzierung der Steuermenge, die während der Ansteuerung der Düsennadel zum Niederdruck abgesondert wird, kann der Wirkungsgrad des Brennstoffeinspritzventils verbessert werden und somit der Gesamtwirkungsgrad der betreffenden Brennstoffeinspritzanlage optimiert werden. Dadurch verringert sich der Energieverbrauch. Außerdem kann auch eine entstehende Verlustwärme, insbesondere im Bereich des Rücklaufs, verringert werden. Dadurch verringert sich die thermische Belastung des Brennstoffeinspritzventils und der anderen Komponenten der Brennstoffeinspritzanlage.By reducing the amount of control discharged to the low pressure during actuation of the nozzle needle, the efficiency of the fuel injector can be improved, thus optimizing the overall efficiency of the particular fuel injection system. This reduces energy consumption. In addition, a resulting heat loss, especially in the area of the return can be reduced. This reduces the thermal load on the fuel injector and the other components of the fuel injection system.
Der Steuerkörper sperrt in der Absperrstellung zumindest eine direkte Verbindung zwischen der Ablaufdrossel und der Zulaufdrossel über den ersten Steuerraumteil. Während der Betätigung der Düsennadel wird somit vermieden, dass unter hohem Druck stehender Brennstoff über die Zulaufdrossel in den ersten Steuerraumteil nachfließt und sogleich aus dem ersten Steuerraumteil über die Ablaufdrossel zum Niederdruck abgesondert wird. In der Absperrstellung sperrt der Steuerkörper zumindest eine direkte Verbindung zwischen der Ablaufdrossel und der Zulaufdrossel über den ersten Steuerraumteil, so dass jedenfalls die direkte Verbindung über den ersten Steuerraumteil gesperrt ist. Je nach Ausgestaltung kann hierbei jedoch noch eine indirekte Verbindung bestehen, insbesondere über eine Fülldrossel und den zweiten Steuerraumteil.The control body locks in the shut-off position at least a direct connection between the outlet throttle and the inlet throttle over the first control chamber part. During actuation of the nozzle needle is thus avoided that under high pressure fuel flows over the inlet throttle in the first control chamber part and is immediately separated from the first control chamber part via the outlet throttle to low pressure. In the shut-off position, the control body blocks at least one direct connection between the outlet throttle and the inlet throttle via the first control chamber part, so that in any case the direct connection via the first control chamber part is blocked. Depending on the configuration, however, an indirect connection may still exist here, in particular via a filling throttle and the second control chamber part.
Vorteilhaft ist es, dass der Steuerkörper eine zweite Stirnseite aufweist, die von der ersten Stirnseite des Steuerkörpers abgewandt ist und dass die zweite Stirnseite einen Brennstoffraum begrenzt, in dem die Düsennadel angeordnet ist. In dem Brennstoffraum, in dem die Düsennadel angeordnet ist, befindet sich im Betrieb unter hohem Druck stehender Brennstoff. Dieser Druck wirkt auf die zweite Stirnseite des Steuerkörpers ein, so dass eine Kraft auf den Steuerkörper wirkt. Diese Kraft wirkt einer Kraft entgegen, die durch den Druck des Brennstoffs im Steuerraum, insbesondere im ersten Steuerraumteil, bedingt ist. Durch eine entsprechende Ausgestaltung des Steuerkörpers, insbesondere die Größe der zweiten Stirnseite, kann somit der Betätigungsvorgang abgestimmt werden. Hierbei können weitere Kräfte, insbesondere eine Vorspannung einer Ventilfeder, wirken.It is advantageous that the control body has a second end face which is remote from the first end face of the control body and that the second end face defines a fuel space in which the nozzle needle is arranged. In the fuel chamber, in which the nozzle needle is arranged, is in operation under high pressure fuel. This pressure acts on the second end face of the control body, so that a force acts on the control body. This force counteracts a force that is due to the pressure of the fuel in the control chamber, in particular in the first control chamber part. By a corresponding embodiment of the control body, in particular the size of second end face, thus the actuation process can be tuned. In this case, further forces, in particular a bias of a valve spring, act.
Vorteilhaft ist es, dass der Steuerkörper an seiner ersten Stirnseite einen Vorsprung aufweist, der in der Absperrstellung zumindest die direkte Verbindung zwischen der Ablaufdrossel und der Zulaufdrossel über den ersten Steuerraumteil sperrt. Hierbei ist es ferner vorteilhaft, dass der Vorsprung des Steuerkörpers in der Absperrstellung einen inneren Bereich des ersten Steuerraumteils von einem äußeren Bereich des ersten Steuerraumteils, der den inneren Bereich ringförmig umgibt, trennt, dass die Ablaufdrossel in den inneren Bereich des ersten Steuerraumteils mündet und dass die Zulaufdrossel in den äußeren Bereich des ersten Steuerraumteils mündet. Hierdurch ist eine vorteilhafte Teilung des ersten Steuerraumteils möglich. Hierbei wirkt in der Absperrstellung der Hochdruck im äußeren Bereich auf die erste Stirnseite des Steuerkörpers ein, die den ersten Steuerraumteil begrenzt. Somit ergibt sich eine Kraft auf den Steuerkörper, die entgegen der Kraft des unter hohem Druck stehenden Brennstoffs im Brennstoffraum, in dem sich die Düsennadel befindet, wirkt. Andererseits ist der innere Bereich des ersten Steuerraumteils über die Ablaufdrossel mit dem Niederdruck verbunden, so dass eine Druckabsenkung im inneren Bereich beziehungsweise ein Hub der Düsennadel ermöglicht wird. Bei dem Hub der Düsennadel verringert sich das Volumen des Steuerraums, insbesondere des zweiten Steuerraumteils, da durch den Hub der Düsennadel das Volumen des zweiten Steuerraumteils in der Sacklochbohrung des Steuerkörpers abnimmt.It is advantageous that the control body has at its first end face a projection which, in the shut-off position, blocks at least the direct connection between the outlet throttle and the inlet throttle via the first control chamber part. In this case, it is further advantageous that the projection of the control body in the shut-off position separates an inner region of the first control chamber part from an outer region of the first control chamber part, which surrounds the inner region in an annular manner, that the outlet throttle opens into the inner region of the first control chamber part and that the inlet throttle opens into the outer region of the first control chamber part. As a result, an advantageous division of the first control room part is possible. In the shut-off position, the high pressure in the outer region acts on the first end face of the control body, which delimits the first control chamber part. This results in a force on the control body, which counteracts the force of the high-pressure fuel in the fuel chamber in which the nozzle needle is located. On the other hand, the inner region of the first control chamber part is connected via the outlet throttle with the low pressure, so that a pressure reduction in the inner region or a stroke of the nozzle needle is made possible. In the stroke of the nozzle needle, the volume of the control chamber, in particular of the second control chamber part decreases because the volume of the second control chamber part decreases in the blind hole of the control body by the stroke of the nozzle needle.
Vorteilhaft ist es ferner, dass an dem Vorsprung ein ringförmiger Absperrsitz ausgestaltet ist und dass ein Durchmesser des ringförmigen Absperrsitzes und ein Nadeldurchmesser der Düsennadel so vorgegeben sind, dass ein Quotient mit einem Dividenden, der gleich dem Durchmesser des ringförmigen Absperrsitzes ist, und einem Divisor, der gleich dem Nadeldurchmesser ist, aus einem Bereich von etwa 0,8 bis etwa 1,5 ist. Durch die Wahl des Durchmessers des ringförmigen Absperrsitzes des Steuerkörpers im Vergleich zum Nadeldurchmesser der Düsennadel kann der Steuerraumdruck definiert werden, ab dem der Dichtsitz am Absperrsitz wieder freigegeben wird. Die Düsennadel wird dann durch hydraulische Kräfte und gegebenenfalls Federkräfte wieder in ihren Sitz gezogen und zieht dabei den Steuerkörper mit. Hierdurch wird der Absperrsitz freigegeben und das Schließen der Düsennadel kann durch die Zulaufdrossel sehr schnell erfolgen.It is furthermore advantageous that an annular shut-off seat is configured on the projection and that a diameter of the annular shut-off seat and a needle diameter of the nozzle needle are predetermined such that a quotient with a dividend equal to the diameter of the annular shut-off seat and a divisor, which is equal to the needle diameter, is in a range of about 0.8 to about 1.5. By choosing the diameter of the annular Absperrsitzes the control body compared to the needle diameter of the nozzle needle, the control chamber pressure can be defined, from which the sealing seat is released at the Absperrsitz again. The nozzle needle is then pulled back into its seat by hydraulic forces and possibly spring forces, thereby pulling the control body. As a result, the Absperrsitz is released and the closing of the nozzle needle can be done very quickly by the inlet throttle.
Vorteilhaft ist es auch, dass die Verbindung zwischen dem ersten Steuerraumteil und dem zweiten Steuerraumteil als gedrosselte Verbindung ausgestaltet ist, dass der Steuerkörper eine gedrosselte Verbindungsbohrung aufweist, die die gedrosselte Verbindung zwischen dem ersten Steuerraumteil und dem zweiten Steuerraumteil bildet, und dass die gedrosselte Verbindungsbohrung des Steuerkörpers in den inneren Bereich des ersten Steuerraumteils mündet. Da die hydraulische Verbindung zwischen dem ersten Steuerraumteil und dem zweiten Steuerraumteil als gedrosselte Verbindung ausgestaltet ist, kann das Freigeben der direkten Verbindung zwischen der Ablaufdrossel und der Zulaufdrossel über den ersten Steuerraumteil durch zusätzliche hydraulische Kräfte auf den Steuerkörper unterstützt werden. Speziell kann das Freigeben des Absperrsitzes an dem Vorsprung des Steuerkörpers durch diese zusätzlichen hydraulischen Kräfte auf den Steuertopf unterstützt werden.It is also advantageous that the connection between the first control chamber part and the second control chamber part is configured as a throttled connection, that the control body has a throttled connection bore, which forms the throttled connection between the first control chamber part and the second control chamber part, and that the throttled connection bore of the control body opens into the inner region of the first control chamber part. Since the hydraulic connection between the first control chamber part and the second control chamber part is configured as a throttled connection, the release of the direct connection between the outlet throttle and the inlet throttle via the first control chamber part can be assisted by additional hydraulic forces on the control body. Specifically, the release of the Absperrsitzes be supported on the projection of the control body by these additional hydraulic forces on the control pot.
Hierbei ist es ferner vorteilhaft, dass der Steuerkörper auf einer Längsachse der Düsennadel angeordnet ist. Zusätzlich oder alternativ ist es vorteilhaft, dass die gedrosselte Verbindungsbohrung auf der Längsachse der Düsennadel angeordnet ist. Zusätzlich oder alternativ ist es vorteilhaft, dass die Ablaufdrossel auf der Längsachse der Düsennadel angeordnet ist. Hierdurch ist eine strömungstechnisch günstige Anordnung realisierbar. Außerdem kann hierdurch ein innerer Bereich des ersten Steuerraumteils im Vergleich zu einem äußeren Bereich des Steuerraumteils auch vergleichsweise klein vorgegeben werden, ohne dass die Dichtwirkung zur Sperrung der direkten Verbindung zwischen der Ablaufdrossel und der Zulaufdrossel über den ersten Steuerraumteil beeinträchtigt wird.In this case, it is also advantageous that the control body is arranged on a longitudinal axis of the nozzle needle. Additionally or alternatively, it is advantageous that the throttled connection bore is arranged on the longitudinal axis of the nozzle needle. Additionally or alternatively, it is advantageous that the outlet throttle is arranged on the longitudinal axis of the nozzle needle. As a result, a fluidically favorable arrangement can be realized. Moreover, as a result, an inner region of the first control chamber part can also be set comparatively small compared to an outer region of the control chamber part, without adversely affecting the sealing effect for blocking the direct connection between the outlet throttle and the inlet throttle via the first control chamber part.
Außerdem ist es vorteilhaft, dass die Zulaufdrossel in den äußeren Bereich des ersten Steuerraumteils mündet, und dass der Steuerkörper eine Fülldrossel aufweist, die einerseits in den äußeren Bereich des ersten Steuerraumteils mündet und die andererseits in den zweiten Steuerraumteil mündet. Durch die Fülldrossel ist eine hydraulische Verbindung zwischen dem äußeren Bereich des ersten Steuerraumteils, in den die Zulaufdrossel mündet, und dem zweiten Steuerraumteil ausgebildet. Hierdurch kann der Beginn des Schließvorgangs beschleunigt werden. Die Fülldrossel kann hierbei über eine Drosselbohrung oder eine ähnlich wirkende hydraulische Verbindung ausgestaltet sein.In addition, it is advantageous that the inlet throttle opens into the outer region of the first control chamber part, and that the control body has a Fülldrossel, which opens on the one hand in the outer region of the first control chamber part and the other opens into the second control chamber part. Through the filling throttle, a hydraulic connection between the outer region of the first control chamber part, in which the inlet throttle opens, and the second control chamber part is formed. As a result, the beginning of the closing process can be accelerated. The filling throttle can be configured via a throttle bore or a similar hydraulic connection.
Vorteilhaft ist es ferner, dass eine Steuerhülse vorgesehen ist, dass der Steuerkörper in einer Führungsbohrung der Steuerhülse geführt ist, dass die Führungsbohrung eine Stufe aufweist, dass der Steuerkörper einen Absatz aufweist und dass der Absatz des Steuerkörpers zur Begrenzung eines Verstellwegs des Steuerkörpers mit der Stufe der Führungsbohrung der Steuerhülse zusammenwirkt. Durch die Einschränkung des Verstellwegs (Hubs) des Steuerkörpers kann eine schnelle Reaktionszeit des Steuerkörpers gewährleistet werden.It is also advantageous that a control sleeve is provided, that the control body is guided in a guide bore of the control sleeve, that the guide bore has a step, that the control body has a paragraph and that the shoulder of the control body to limit a displacement of the control body with the step the guide bore of the control sleeve cooperates. By limiting the displacement (stroke) of the control body, a fast reaction time of the control body can be ensured.
Vorteilhaft ist es auch, dass die erste Stirnseite des Steuerkörpers einer Seite einer Drosselplatte zugewandt ist, dass der Steuerkörper einen Vorsprung aufweist, dass an demIt is also advantageous that the first end face of the control body faces one side of a throttle plate, that the control body has a projection that on the
Vorsprung ein Absperrsitz ausgestaltet ist, dass der Absperrsitz des Vorsprungs in der Absperrstellung des Steuerkörpers mit der Seite der Drosselplatte zusammenwirkt, um zumindest die direkte Verbindung zwischen der Ablaufdrossel und der Zulaufdrossel über den ersten Steuerraumteil zu sperren, dass zwischen der ersten Stirnseite des Steuerkörpers und der Seite der Drosselplatte ein Federelement angeordnet ist und dass das Federelement in der Absperrstellung des Steuerkörpers vorgespannt ist. Das Federelement kann beispielsweise durch eine Blattfeder ausgebildet sein. Durch das Federelement kann eine Ausgangsstellung des Steuerkörpers vorgegeben werden. Dadurch sind die Startbedingungen immer sauber definiert.Projection is designed a shut-off seat, that the Absperrsitz the projection in the shut-off position of the control body cooperates with the side of the throttle plate to lock at least the direct connection between the outlet throttle and the inlet throttle over the first control chamber part that between the first end face of the control body and the Side of the throttle plate, a spring element is arranged and that the spring element is biased in the shut-off position of the control body. The spring element may be formed for example by a leaf spring. By the spring element, a starting position of the control body can be specified. As a result, the starting conditions are always defined clean.
Bevorzugte Ausführungsbeispiele der Erfindung sind in der nachfolgenden Beschreibung unter Bezugnahme auf die beigefügten Zeichnungen, in denen sich entsprechende Elemente mit übereinstimmenden Bezugszeichen versehen sind, näher erläutert. Es zeigt:
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Fig. 1 ein Brennstoffeinspritzventil in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem ersten Ausführungsbeispiel der Erfindung; -
Fig. 2 ein Diagramm zur Erläuterung der Funktionsweise eines Brennstoffeinspritzventils entsprechend einer möglichen Ausgestaltung; -
Fig. 3 ein Brennstoffeinspritzventil in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem zweiten Ausführungsbeispiel der Erfindung.
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Fig. 1 a fuel injection valve in an excerpt, schematic sectional view according to a first embodiment of the invention; -
Fig. 2 a diagram for explaining the operation of a fuel injection valve according to a possible embodiment; -
Fig. 3 a fuel injection valve in a partial, schematic sectional view according to a second embodiment of the invention.
Das Brennstoffeinspritzventil 1 weist ein Gehäuse 2 und eine Drosselplatte 3 auf, die auf geeignete Weise in das Gehäuse 2 eingesetzt ist. In dem Gehäuse 2 ist ein Brennstoffraum 4 ausgestaltet, in dem eine Düsennadel 5 angeordnet ist. Außerdem weist das Brennstoffeinspritzventil 1 ein Steuerventil 6 auf, das über einen Aktor 7 betätigbar ist, wie es durch einen Doppelpfeil 8 veranschaulicht ist. Der Aktor 7 kann beispielsweise als Magnetaktor 7 oder als piezoelektrischer Aktor 7 ausgestaltet sein.The fuel injection valve 1 has a
Durch das Gehäuse 2 des Brennstoffeinspritzventils 1 ist eine Hochdruckleitung 9 geführt. Der Hochdruckleitung 9 wird unter hohem Druck stehender Brennstoff, der beispielsweise einem Common-Rail entnommen wird, zugeführt. Die Drosselplatte 3 weist eine Bohrung 10 auf, über die der unter hohem Druck stehende Brennstoff aus der Hochdruckleitung 9 in den Brennstoffraum 4 geführt wird.Through the
Die Drosselplatte 3 weist außerdem eine Ablaufdrossel 11 und eine Zulaufdrossel 12 auf. Die Zulaufdrossel 12 zweigt von der Hochdruckleitung 9 ab. Die Ablaufdrossel 11 führt zu dem Steuerventil 6.The
Das Brennstoffeinspritzventil 1 weist ferner eine Steuerhülse 15 auf, an der eine Führungsbohrung 16 ausgestaltet ist. Die Führungsbohrung 16 ist in diesem Ausführungsbeispiel als zylinderförmige Führungsbohrung 16 ausgestaltet. In der Führungsbohrung 16 der Steuerhülse 15 ist ein Steuerkörper 17 entlang einer Längsachse 18 geführt.The fuel injection valve 1 also has a
Die Steuerhülse 15 weist eine Sacklochbohrung 19 auf. Ein Ende 20 der Düsennadel 5 ist in der Sacklochbohrung 19 entlang der Längsachse 18 geführt.The
Der Steuerkörper 17 weist eine erste Stirnseite 21 und eine zweite Stirnseite 22 auf, die voneinander abgewandt sind. Der Steuerkörper 17 weist an der ersten Stirnseite 21 einen Vorsprung 23 auf, der als ringförmiger Vorsprung 23 ausgestaltet ist. An dem ringförmigen Vorsprung 23 ist ein ringförmiger Absperrsitz 24 ausgestaltet, der in diesem Ausführungsbeispiel als kreisringförmiger, insbesondere kreislinienförmiger, Absperrsitz 24 ausgestaltet ist. Der Vorsprung 23 unterteilt die erste Stirnseite 21 des Steuerkörpers 17 in eine äußere Fläche 25 und eine innere Fläche 26. Die äußere Fläche 25 ist als kreisringförmige Fläche 25 ausgestaltet. Die innere Fläche 26 ist als kreisförmige Fläche 26 ausgestaltet.The
Das Brennstoffeinspritzventil 1 weist einen Steuerraum 30 auf. Der Steuerraum 30 umfasst einen ersten Steuerraumteil 31 und einen zweiten Steuerraumteil 32. In der in der
Somit begrenzt die erste Stirnseite 21 des Steuerkörpers 17 den ersten Steuerraumteil 31 des Steuerraums 30. Die Stirnseite 36 der Düsennadel 5 begrenzt in der Sacklochbohrung 19 den zweiten Steuerraumteil 32 des Steuerraums 30. Der erste Steuerraumteil 31 ist mit dem zweiten Steuerraumteil 32 über eine Verbindungsbohrung 38 verbunden. Hierbei ist in der in der
Die Ablaufdrossel 11 und die Zulaufdrossel 12 münden in den ersten Steuerraumteil 31. Hierbei mündet die Ablaufdrossel 11 in den inneren Bereich 34, während die Zulaufdrossel 12 in den äußeren Bereich 33 mündet. In der Absperrstellung des Steuerkörpers 17 ist somit eine direkte Verbindung zwischen der Ablaufdrossel 11 und der Zulaufdrossel 12 über den ersten Steuerraumteil 31 gesperrt. In diesem Ausführungsbeispiel besteht keine indirekte Verbindung zwischen der Ablaufdrossel 11 und der Zulaufdrossel 12.The
Die Ausgestaltung und Funktionsweise des Brennstoffeinspritzventils 1 ist im Folgenden auch anhand der
Im Betrieb des Brennstoffeinspritzventils 1 befindet sich im Brennstoffraum 4 unter hohem Druck stehender Brennstoff. Der Druck des Brennstoffs im Brennstoffraum 4 wirkt hierbei über die zweite Stirnseite 22 des Steuerkörpers 17 auf den Steuerkörper 17 ein. Ferner befindet sich auch im Steuerraum 30 unter hohem Druck stehender Brennstoff. Der Druck des Brennstoffs wirkt im Bereich des ersten Steuerraumteils 31 auf die erste Stirnseite 21 des Steuerkörpers 17 ein. Hierbei erfolgt eine teilweise Kompensation, da der Druck im zweiten Steuerraumteil 32 in entgegengesetzter Richtung auf die Fläche 37 einwirkt. Hierbei ist anzumerken, dass sich in der Ausgangsstellung der Steuerkörper 17 in einem ausreichenden Abstand zur Seite 35 der Drosselplatte 3 befindet, so dass der ringförmige Absperrsitz 24 am Vorsprung 23 geöffnet ist und der innere Bereich 34 und der äußere Bereich 33 des ersten Steuerraumteils 31 nicht voneinander getrennt, sondern miteinander verbunden sind.In operation of the fuel injection valve 1 is located in the
Zum Zeitpunkt t1 betätigt der Aktor 7 das Steuerventil 6. Hierdurch wird die Ablaufdrossel 11 freigegeben und Brennstoff kann aus dem Steuerraum 30 zum Niederdruck abfließen. Der Druck im Steuerraum 30 fällt hierbei etwas ab. Kurz nach dem Zeitpunkt t1, nämlich zum Zeitpunkt t2, bewegt sich daher der Steuerkörper 17 in einer Richtung 43. Denn an der zweiten Stirnseite 22 des Steuerkörpers 17 liegt weiterhin der Hochdruck des Brennstoffs im Brennstoffraum 4 an. Durch den reduzierten Druck im Steuerraum 30 verringert sich auch die an der Stirnseite 36 der Düsennadel 5 wirkende Druckbeaufschlagung. Dadurch bewegt sich auch die Düsennadel 5 in der Richtung 43. Allerdings schlägt die Steuerhülse 15 mit ihrem Vorsprung 23 an der Seite 35 der Drosselplatte 3 an, so dass der äußere Bereich 33 des ersten Steuerraumteils 31 von dem inneren Bereich 34 des ersten Steuerraumteils 31 getrennt wird. Ein Nachfließen von Brennstoff aus der Hochdruckleitung 9 über die Zulaufdrossel 12 in den inneren Bereich 34 des Steuerraums 30 ist somit unterbunden. Der über die Ablaufdrossel 11 abfließende Brennstoff bedingt somit ein schnelles Öffnen der Düsennadel 5.At time t1, the
Somit gelangt der Steuerkörper 17 rasch in seine Absperrstellung, so dass während der Öffnungsbewegung der Düsennadel 5, das heißt zwischen dem Zeitpunkt t2 und dem Zeitpunkt t3 kein Durchfluss von Brennstoff durch die Zulaufdrossel 12 erfolgt oder solch ein Durchfluss zumindest vernachlässigbar ist, wie es speziell bei dem anhand der
Dann kann der Steuerkörper 17 im Vergleich zur Öffnungsbewegung der Düsennadel 5 noch schneller in die Absperrstellung verstellt werden.Then, the
Etwas vor dem Zeitpunkt t3 wird das Steuerventil 6 wieder geschlossen, so dass der Brennstofffluss durch die Ablaufdrossel 11 unterbrochen wird. Nach dem Zeitpunkt t3 beginnt deshalb die Schließbewegung der Düsennadel 5, bei der sich die Düsennadel 5 entgegen der Richtung 43 bewegt. Um den Druck im Steuerraum 30 aufzubauen und den Brennstoff entsprechend dem sich nun vergrößernden Volumen des Steuerraums 30 nachzufüllen, muss jetzt Brennstoff über die Zulaufdrossel 12 nachfließen. Dies erfolgt ab dem Zeitpunkt t4. Beispielsweise kann zum Zeitpunkt t5 das Steuerventil 6 wieder vollständig geschlossen sein, so dass die Ablaufdrossel 11 gesperrt ist. Bis zum vollständigen Schließen der Düsennadel 5, das heißt bis zum Zeitpunkt t6 nimmt das Volumen des Steuerraums 30 noch zu, so dass bis zum Zeitpunkt t6 unter hohem Druck stehender Brennstoff über die Zulaufdrossel 12 in den Steuerraum 30 fließt. Wenn die Düsennadel 5 dann ihre Endposition (Schließstellung) erreicht hat, dann endet auch der Nachfluss von Brennstoff durch die Zulaufdrossel 12. Dies ist zum Zeitpunkt t6 der Fall.Somewhat before the time t3, the
Durch den Zufluss des Brennstoffs über die Zulaufdrossel 12 wird auch der Steuerkörper 17 aufgedrückt. Denn der Brennstoff fließt über die Zulaufdrossel 12 zunächst in den äußeren Bereich 33, so dass über das zufließende Volumen automatisch eine Verstellung des Steuerkörpers 17 entgegen der Richtung 43 erfolgen muss.By the inflow of the fuel via the
Wesentlich ist somit die Sperrung des Durchflusses 32 durch die Zulaufdrossel 12 während der Öffnungsphase der Düsennadel 5, das heißt zwischen dem Zeitpunkt t2 und dem Zeitpunkt t3. Ohne die Sperrfunktion des Steuerkörpers 17 würde es bereits mit der Öffnung der Düsennadel 5 zu einem Nachfluss von Brennstoff über die Zulaufdrossel 12 kommen. Dadurch würde sich die Steuermenge erheblich vergrößern. Die zusätzliche Steuermenge würde dann über die Ablaufdrossel 11 zum Niederdruck abfließen. Bei der Ausgestaltung entsprechend dem Ausführungsbeispiel, wie es in dem Diagramm der
Bei dem anhand der
Durch die Wahl eines Durchmessers (Sitzdurchmessers) 50 des ringförmigen Absperrsitzes 24 des Steuerkörpers 17 im Vergleich zu einem Nadeldurchmesser 51 der Düsennadel 5 kann der Steuerraumdruck vorgegeben werden, ab dem der Dichtsitz am ringförmigen Absperrsitz 24 des Steuerkörpers 17 wieder freigegeben wird. Vorteilhafte Werte für den Durchmesser 50 des ringförmigen Absperrsitzes 24 sind das 0,8-fache bis das 1,5-fache des Nadeldurchmessers 51. Der Durchmesser 50 des ringförmigen Absperrsitzes 24 und der Nadeldurchmesser 51 der Düsennadel 5 sind somit vorzugsweise so vorgegeben, dass ein Quotient mit einem Dividenden, der gleich dem Durchmesser 50 des ringförmigen Absperrsitzes 24 ist, und einem Divisor, der gleich dem Nadeldurchmesser 51 ist, aus einem Bereich von etwa 0,8 bis etwa 1,5 ist.By selecting a diameter (seat diameter) 50 of the
Die Düsennadel 5 wird durch hydraulische Kräfte und gegebenenfalls Federkräfte entgegen der Richtung 43 betätigt, wobei der Steuerkörper 17 mitverstellt wird. Dadurch wird der Dichtsitz am ringförmigen Absperrsitz 24 freigegeben und das Schließen der Düsennadel 5 kann durch Nachfließen von unter hohem Druck stehenden Brennstoff über die Zulaufdrossel 12 sehr schnell erfolgen. Wenn die Verbindungsbohrung 38 als gedrosselte Verbindungsbohrung ausgestaltet ist, dann kann das Freigeben des Absperrsitzes 24 durch zusätzliche hydraulische Kräfte auf den Steuerkörper 17 unterstützt werden.The
Der Steuerkörper 17 ist in der Führungsbohrung 16 frei bewegbar beziehungsweise verschiebbar gelagert. Der Steuerkörper 17 ist in diesem Ausführungsbeispiel als topfförmiger Steuerkörper 17, das heißt als Steuertopf 17, ausgestaltet.The
Außerdem ist in diesem Ausführungsbeispiel ein Federelement 59 vorgesehen, das zwischen der ersten Stirnseite 21 des Steuerkörpers 17 und der Seite 35 der Drosselplatte 3 angeordnet. Durch das Federelement 59, das als Tellerfeder 59 ausgestaltet sein kann, ist eine definierte Ausgangsposition des Steuerkörpers 17 vorgegeben.In addition, in this embodiment, a
Somit kann eine schnelle Reaktionszeit des Steuerkörpers 17 beim Freigeben der Ablaufdrossel 11 über das Steuerventil 6 gewährleistet werden. Die Reaktionszeit wird hierbei durch den vorgegebenen maximalen Verstellweg 58 begrenzt. Je nach Ausgestaltung kann das Federelement 59 den Steuerkörper 17 auch in der Richtung 43 mit einer Vorspannung beaufschlagen.Thus, a fast reaction time of the
Über die Fülldrossel 55 ist eine hydraulische Verbindung zwischen dem äußeren Bereich 33 des ersten Steuerraumteils 31 und dem zweiten Steuerraumteil 32 gebildet, wodurch der Beginn des Schließvorgangs beschleunigt werden kann.Via the filling throttle 55, a hydraulic connection between the outer region 33 of the first control chamber part 31 and the second control chamber part 32 is formed, whereby the beginning of the closing process can be accelerated.
In diesem Ausführungsbeispiel sperrt der Steuerkörper 17 in der Absperrstellung eine direkte Verbindung zwischen dem äußeren Bereich 33 und dem inneren Bereich 34 des ersten Steuerraumteils 31. Über die Fülldrossel 55, den zweiten Steuerraumteil 32 und die Verbindungsbohrung 38 ist allerdings eine indirekte Verbindung gegeben. In der Absperrstellung sind die Fülldrossel 55 und die gedrosselte Verbindungsbohrung 38 allerdings hintereinander geschaltet, so dass der beim Öffnen der Düsennadel 5 gegebenenfalls mögliche Durchfluss 42 durch die Zulaufdrossel 12 vernachlässigbar ist. Daher ergibt sich auch bei dieser Ausgestaltung eine Situation, wie sie beispielsweise anhand des in
Somit kann die Zulaufdrossel 12 bei geöffnetem Steuerventil 6 zumindest zeitweise verschlossen werden oder es kann zumindest eine Reduzierung der zugeführten Hochdruckmenge erreicht werden. Bei geschlossenem Steuerventil 6 wird die Zulaufdrossel 12 wieder freigegeben. Somit kann eine permanente Verbindung zwischen dem Hochdruckbereich und dem Niederdruckbereich wesentlich gedämpft oder ganz vermieden werden. Somit kann die Steuermenge deutlich reduziert werden. Hierdurch kann auch die Temperatur im Rücklauf reduziert werden. Ein weiterer Vorteil besteht darin, dass die Drosselwirkung der Ablaufdrossel 11 und die Drosselwirkung der Zulaufdrossel 12 innerhalb gewisser Grenzen frei gewählt werden können. Dadurch ist eine flexible Vorgabe der Öffnungs- und Schließgeschwindigkeit der Düsennadel 5 möglich. Ferner kann der Wirkungsgrad des Brennstoffeinspritzventils 1 verbessert werden, da der Durchfluss 42 durch die Zulaufdrossel 12 zeitlich begrenzt ist und somit die Steuermenge reduziert ist. Dadurch können auch geringere Kohlendioxidemissionen eines Kraftfahrzeugs oder dergleichen erreicht werden.Thus, the
Die Erfindung ist nicht auf die beschriebenen Ausführungsbeispiele beschränkt.The invention is not limited to the described embodiments.
Claims (10)
- Fuel injection valve (1), in particular injector for fuel injection systems of air-compressing, auto-ignition internal combustion engines, having a control valve (6), having a control chamber (30) and having a nozzle needle (5), wherein an outflow throttle (11) and an inflow throttle (12) for the control chamber (30) are provided, and wherein the control valve (6) serves for controlling a flow through the outflow throttle (11), wherein a control body (17) is provided, and the control body (17) has a first face side (21) which delimits a first control chamber part (31) of the control chamber (30), and the outflow throttle (11) and the inflow throttle (12) issue into the first control chamber part (31), and the control body (17), in a shut-off position, blocks at least a direct connection between the outflow throttle (11) and the inflow throttle (12) via the first control chamber part (31),
characterized
in that the control body (17) has a blind bore (19) in which one end (20) of the nozzle needle (5) is guided, and in that the nozzle needle (5) has, at the end (20) guided in the blind bore (19), a face side (36) which, in the blind bore (19), delimits a second control chamber part (32) of the control chamber (30). - Fuel injection valve according to Claim 1,
characterized
in that the control body (17) has a second face side (22) which is averted from the first face side (21) of the control body (17), and in that the second face side (22) delimits a fuel chamber (4) in which the nozzle needle (5) is arranged. - Fuel injection valve according to Claim 1 or 2,
characterized
in that the control body (17) has, on its first face side (21), a projection (23) which, in the shut-off position, blocks at least the direct connection between the outflow throttle (11) and the inflow throttle (12) via the first control chamber part (31). - Fuel injection valve according to Claim 3,
characterized
in that, in the shut-off position, the projection (23) of the control body (17) separates an inner region (34) of the first control chamber part (31) from an outer region (33) of the first control chamber part (31), which outer region annularly surrounds the inner region (34), in that the outflow throttle (11) issues into the inner region (34) of the first control chamber part (31), and in that the inflow throttle (12) issues into the outer region (33) of the first control chamber part (31). - Fuel injection valve according to Claim 4,
characterized
in that an annular shut-off seat (24) is formed on the projection (23), and in that a diameter (50) of the annular shut-off seat (24) and a needle diameter (51) of the nozzle needle (5) are predefined such that a quotient with a dividend equal to the diameter (50) of the annular shut-off seat (24) and a divisor equal to the needle diameter (51) is in a range from approximately 0.8 to approximately 1.5. - Fuel injection valve according to one of Claims 1 to 5,
characterized
in that the connection between the first control chamber part (31) and the second control chamber part (32) is in the form of a throttled connection, in that the control body (17) has a throttled connecting bore (38) which forms the throttled connection between the first control chamber part (31) and the second control chamber part (32), and in that the throttled connecting bore (38) of the control body (17) issues into an inner region (34) of the first control chamber part (31). - Fuel injection valve according to Claim 6,
characterized
in that the control body (17) is arranged at least approximately on a longitudinal axis (18) of the nozzle needle (5), and/or in that the throttled connecting bore (38) is arranged at least approximately on the longitudinal axis (18) of the nozzle needle (5) and/or in that the outflow throttle (11) is arranged at least approximately on the longitudinal axis (18) of the nozzle needle (5). - Fuel injection valve according to one of Claims 1 to 7,
characterized
in that the inflow throttle (12) issues into an outer region (33) of the first control chamber part (31), and in that the control body (17) has a fill throttle (55) which issues at one side into the outer region (33) of the first control chamber part (31) and at the other side into the second control chamber part (32). - Fuel injection valve according to one of Claims 1 to 8,
characterized
in that a control sleeve (15) is provided, in that the control body (17) is guided in a guide bore (16) of the control sleeve (15), in that the guide bore (16) has a step (56), in that the control body (17) has a shoulder (57), and in that the shoulder (57) of the control body (17) interacts with the step (56) of the guide bore (16) of the control sleeve (15) in order to delimit an adjustment travel (58) of the control body (17). - Fuel injection valve according to one of Claims 1 to 9,
characterized
in that the first face side (21) of the control body (17) faces toward a side (35) of a throttle plate (3), in that the control body (17) has a projection (23), in that a shut-off seat (24) is formed on the projection (23), in that, in the shut-off position of the control body (17), the shut-off seat (24) of the projection (23) interacts with the side (35) of the throttle plate (3) so as to block at least the direct connection between the outflow throttle (11) and the inflow throttle (12) via the first control chamber part (31), in that a spring element (59) is arranged between the first face side (21) of the control body (17) and the side (35) of the throttle plate (3), and in that the spring element (59) is prestressed when the control body (17) is in the shut-off position.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE201210202549 DE102012202549A1 (en) | 2012-02-20 | 2012-02-20 | Fuel injector |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2628938A1 EP2628938A1 (en) | 2013-08-21 |
EP2628938B1 true EP2628938B1 (en) | 2015-04-15 |
Family
ID=47561473
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20130152149 Not-in-force EP2628938B1 (en) | 2012-02-20 | 2013-01-22 | Fuel injector valve |
Country Status (2)
Country | Link |
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EP (1) | EP2628938B1 (en) |
DE (1) | DE102012202549A1 (en) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10077748B2 (en) | 2014-12-23 | 2018-09-18 | Cummins Inc. | Fuel injector for common rail |
DE102015226070A1 (en) | 2015-12-18 | 2017-06-22 | Robert Bosch Gmbh | fuel injector |
CN106762291A (en) * | 2017-01-18 | 2017-05-31 | 哈尔滨工程大学 | A kind of board-like electric-controlled fuel injector of minute hand valve opening without static leakage |
CN106593726A (en) * | 2017-01-18 | 2017-04-26 | 哈尔滨工程大学 | Resonant electrically controlled oil injector with oil fed through double paths |
CN106677942A (en) * | 2017-01-18 | 2017-05-17 | 哈尔滨工程大学 | Two-way oil inlet long-needle-valve hole-plate type electronic control fuel injector without static leakage |
DE102017207845A1 (en) * | 2017-05-10 | 2018-11-15 | Robert Bosch Gmbh | Valve for metering a fluid |
EP3722590A4 (en) * | 2017-12-07 | 2021-07-28 | Tianjin Shengoumei Engine Technology Consulting Co | Common-rail fuel injector for diesel engine |
JP2023504727A (en) * | 2019-12-03 | 2023-02-06 | ガンサー-ハイドロマグ アーゲー | Fuel injection valve with slide valve for internal combustion engine |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10139623A1 (en) | 2001-08-11 | 2003-02-27 | Bosch Gmbh Robert | Injection arrangement for fuel storage injection system has bypass channel from high-pressure chamber to valve chamber closed by valve closure element during injection process |
DE502004008540D1 (en) * | 2003-08-22 | 2009-01-08 | Ganser Hydromag | PILOT VALVE CONTROLLED FUEL INJECTION VALVE |
CN102828872B (en) * | 2006-03-03 | 2015-09-02 | 甘瑟-许德罗玛格股份公司 | The Fuelinjection nozzle of internal-combustion engine |
JP5152220B2 (en) * | 2010-02-18 | 2013-02-27 | 株式会社デンソー | Fuel injection device |
-
2012
- 2012-02-20 DE DE201210202549 patent/DE102012202549A1/en not_active Withdrawn
-
2013
- 2013-01-22 EP EP20130152149 patent/EP2628938B1/en not_active Not-in-force
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DE102012202549A1 (en) | 2013-08-22 |
EP2628938A1 (en) | 2013-08-21 |
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