EP2628938B1 - Soupape d'injection de combustible - Google Patents

Soupape d'injection de combustible Download PDF

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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
Application number
EP20130152149
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German (de)
English (en)
Other versions
EP2628938A1 (fr
Inventor
Wolfgang Stoecklein
Volker Beuche
Bernd Berghaenel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Publication date
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Publication of EP2628938A1 publication Critical patent/EP2628938A1/fr
Application granted granted Critical
Publication of EP2628938B1 publication Critical patent/EP2628938B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • 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
    • 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
    • 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
    • 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)

Claims (10)

  1. Soupape d'injection de carburant (1), en particulier injecteur pour systèmes d'injection de carburant de moteurs à combustion interne à auto-allumage et à compression d'air, comprenant une soupape de commande (6), un espace de commande (30) et une aiguille d'injecteur (5), un étranglement d'évacuation (11) et un étranglement d'admission (12) pour l'espace de commande (30) étant prévus, et la soupape de commande (6) servant à commander un écoulement à travers l'étranglement d'évacuation (11), un corps de commande (17) étant prévu et le corps de commande (17) comprenant un premier côté frontal (21) qui limite une première partie d'espace de commande (31) de l'espace de commande (30), et l'étranglement d'évacuation (11) et l'étranglement d'admission (12) débouchant dans la première partie d'espace de commande (31) et le corps de commande (17) bloquant, dans une position de blocage, au moins une liaison directe entre l'étranglement d'évacuation (11) et l'étranglement d'admission (12) par le biais de la première partie d'espace de commande (31),
    caractérisée en ce que
    le corps de commande (17) comprend un alésage borgne (19) dans lequel une extrémité (20) de l'aiguille d'injecteur (5) est guidée, et en ce que l'aiguille d'injecteur (5) comprend un côté frontal (36) à l'extrémité (20) guidée dans l'alésage borgne (19), lequel côté frontal limite une deuxième partie d'espace de commande (32) de l'espace de commande (30) dans l'alésage borgne (19).
  2. Soupape d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    le corps de commande (17) comprend un deuxième côté frontal (22) qui est opposé au premier côté frontal (21) du corps de commande (17), et en ce que le deuxième côté frontal (22) limite un espace de carburant (4) dans lequel l'aiguille d'injecteur (5) est disposée.
  3. Soupape d'injection de carburant selon la revendication 1 ou 2,
    caractérisée en ce que
    le corps de commande (17) comprend une saillie (23) sur son premier côté frontal (21), laquelle saillie bloque, dans la position de blocage, au moins la liaison directe entre l'étranglement d'évacuation (11) et l'étranglement d'admission (12) par le biais de la première partie d'espace de commande (31).
  4. Soupape d'injection de carburant selon la revendication 3,
    caractérisée en ce que,
    dans la position de blocage, la saillie (23) du corps de commande (17) sépare une région intérieure (34) de la première partie d'espace de commande (31) d'une région extérieure (33) de la première partie d'espace de commande (31) qui entoure de manière annulaire la région intérieure (34), en ce que l'étranglement d'évacuation (11) débouche dans la région intérieure (34) de la première partie d'espace de commande (31) et en ce que la soupape d'admission (12) débouche dans la région extérieure (33) de la première partie d'espace de commande (31).
  5. Soupape d'injection de carburant selon la revendication 4,
    caractérisée en ce
    qu'un siège de blocage annulaire (24) est configuré sur la saillie (23), et en ce qu'un diamètre (50) du siège de blocage annulaire (24) et un diamètre d'aiguille (51) de l'aiguille d'injecteur (5) sont prédéfinis de telle sorte qu'un quotient obtenu à partir d'un dividende qui est égal au diamètre (50) du siège de blocage annulaire (24) et d'un diviseur qui est égal au diamètre d'aiguille (51) soit dans une plage d'approximativement 0,8 à approximativement 1,5.
  6. Soupape d'injection de carburant selon l'une quelconque des revendications 1 à 5,
    caractérisée en ce que
    la liaison entre la première partie d'espace de commande (31) et la deuxième partie d'espace de commande (32) est configurée sous forme de liaison étranglée, en ce que le corps de commande (17) comprend un alésage de liaison étranglé (38) qui forme la liaison étranglée entre la première partie d'espace de commande (31) et la deuxième partie d'espace de commande (32), et en ce que l'alésage de liaison étranglé (38) du corps de commande (17) débouche dans une région intérieure (34) de la première partie d'espace de commande (31).
  7. Soupape d'injection de carburant selon la revendication 6,
    caractérisée en ce que
    le corps de commande (17) est disposé au moins approximativement sur un axe longitudinal (18) de l'aiguille d'injecteur (5) et/ou en ce que l'alésage de liaison étranglé (38) est disposé au moins approximativement sur l'axe longitudinal (18) de l'aiguille d'injecteur (5) et/ou en ce que l'étranglement d'évacuation (11) est disposé au moins approximativement sur l'axe longitudinal (18) de l'aiguille d'injecteur (5).
  8. Soupape d'injection de carburant selon l'une quelconque des revendications 1 à 7,
    caractérisée en ce que
    l'étranglement d'admission (12) débouche dans une région extérieure (33) de la première partie d'espace de commande (31), en ce que le corps de commande (17) comprend un étranglement de remplissage (55) qui débouche d'une part dans la région extérieure (33) de la première partie d'espace de commande (31) et qui débouche d'autre part dans la deuxième partie d'espace de commande (32).
  9. Soupape d'injection de carburant selon l'une quelconque des revendications 1 à 8,
    caractérisée en ce
    qu'une douille de commande (15) est prévue, en ce que le corps de commande (17) est guidé dans un alésage de guidage (16) de la douille de commande (15), en ce que l'alésage de guidage (16) comprend un gradin (56), en ce que le corps de commande (17) comprend un épaulement (57) et en ce que l'épaulement (57) du corps de commande (17) coopère avec le gradin (56) de l'alésage de guidage (16) de la douille de commande (15) pour limiter une course de déplacement (58) du corps de commande (17).
  10. Soupape d'injection de carburant selon l'une quelconque des revendications 1 à 9,
    caractérisée en ce que
    le premier côté frontal (21) du corps de commande (17) est tourné vers un côté (35) d'une plaque d'étranglement (3), en ce que le corps de commande (17) comprend une saillie (23), en ce qu'un siège de blocage (24) est configuré sur la saillie (23), en ce que, dans la position de blocage du corps de commande (17), le siège de blocage (24) de la saillie (23) coopère avec le côté (35) de la plaque d'étranglement (3), pour bloquer au moins la liaison directe entre l'étranglement d'évacuation (11) et l'étranglement d'admission (12) par le biais de la première partie d'espace de commande (31), en ce qu'un élément de ressort (59) est disposé entre le premier côté frontal (21) du corps de commande (17) et le côté (35) de la plaque d'étranglement (3) et en ce que l'élément de ressort (59) est précontraint dans la position de blocage du corps de commande (17).
EP20130152149 2012-02-20 2013-01-22 Soupape d'injection de combustible Not-in-force EP2628938B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201210202549 DE102012202549A1 (de) 2012-02-20 2012-02-20 Brennstoffeinspritzventil

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EP2628938A1 EP2628938A1 (fr) 2013-08-21
EP2628938B1 true EP2628938B1 (fr) 2015-04-15

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Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10077748B2 (en) 2014-12-23 2018-09-18 Cummins Inc. Fuel injector for common rail
DE102015226070A1 (de) 2015-12-18 2017-06-22 Robert Bosch Gmbh Kraftstoffinjektor
CN106762291A (zh) * 2017-01-18 2017-05-31 哈尔滨工程大学 一种无静态泄漏的长针阀孔板式电控喷油器
CN106677942A (zh) * 2017-01-18 2017-05-17 哈尔滨工程大学 一种无静态泄漏的双路进油长针阀孔板式电控喷油器
CN106593726A (zh) * 2017-01-18 2017-04-26 哈尔滨工程大学 双路进油谐振式电控喷油器
DE102017207845A1 (de) * 2017-05-10 2018-11-15 Robert Bosch Gmbh Ventil zum Zumessen eines Fluids
WO2019109825A1 (fr) * 2017-12-07 2019-06-13 天津盛欧美发动机技术有限公司 Injecteur de carburant à rail commun pour moteur diesel
CN114761681B (zh) * 2019-12-03 2024-01-16 甘瑟-许德罗玛格股份公司 用于内燃机的具有滑阀的燃料喷射阀

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10139623A1 (de) 2001-08-11 2003-02-27 Bosch Gmbh Robert Einspritzanordnung für ein Kraftstoff-Speichereinspritzsystem
EP1656498B1 (fr) * 2003-08-22 2008-11-26 Ganser-Hydromag Ag Soupape d'injection de carburant commandee par une soupape pilote
CN101395366B (zh) * 2006-03-03 2012-09-12 甘瑟-许德罗玛格股份公司 内燃机的燃料喷射阀
JP5152220B2 (ja) * 2010-02-18 2013-02-27 株式会社デンソー 燃料噴射装置

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EP2628938A1 (fr) 2013-08-21

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