EP2053235B1 - Combustion engine with fuel injectors - Google Patents

Combustion engine with fuel injectors Download PDF

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Publication number
EP2053235B1
EP2053235B1 EP08017534.2A EP08017534A EP2053235B1 EP 2053235 B1 EP2053235 B1 EP 2053235B1 EP 08017534 A EP08017534 A EP 08017534A EP 2053235 B1 EP2053235 B1 EP 2053235B1
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EP
European Patent Office
Prior art keywords
clamping claw
cylinder head
clamping
combustion engine
fuel injection
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.)
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Application number
EP08017534.2A
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German (de)
French (fr)
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EP2053235A2 (en
EP2053235A3 (en
Inventor
Martin Biener
Andreas Schüller
Ingo KÜHNE
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.)
Volkswagen AG
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Volkswagen AG
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Publication of EP2053235A2 publication Critical patent/EP2053235A2/en
Publication of EP2053235A3 publication Critical patent/EP2053235A3/en
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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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/14—Arrangements of injectors with respect to engines; Mounting of injectors
    • 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
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/803—Fuel injection apparatus manufacture, repair or assembly using clamp elements and fastening means; e.g. bolts or screws

Definitions

  • the invention relates to an internal combustion engine, in particular a diesel engine, in particular a motor vehicle, having at least two working cylinders and a cylinder head closing the working cylinder, in which a fuel injector is arranged for each working cylinder, wherein for each at least two fuel injectors a clamping claw with at least two arms is provided such in that one arm of the clamping claw acts on a fuel injection device and presses the respective fuel injection device against a seat in the cylinder head with a predetermined force, wherein a fastening means is provided, which fixes the clamping claw to the cylinder head, according to the preamble of claim 1.
  • the nozzle clamping device has contact parts which rest on terminal receiving seats of the fuel injection nozzles. Between the contact parts, the nozzle clamping device has a bolt insertion hole into which a clamping bolt is inserted to exert a pressure against the fuel injection nozzles and deliver sealing loads.
  • the nozzle clamp includes a clearance that reduces the pressure force on the fuel injectors such that at a predetermined degree of bolt attraction force, a substantially equal compressive force occurs on the three fuel injectors.
  • the nozzle clamping device is made of a spring material such that the nozzle clamping device is slightly bent.
  • the invention is based on the object, an internal combustion engine og. Improve the way of installation and ease of maintenance.
  • the arms of the clamping claw and / or the fastening means is or are such that above the predetermined force for the pressure of the fuel injectors against subject the respective seat in the cylinder head, the arms of the clamping claw and / or the fastening means of a plastic deformation.
  • the fastening means for at least one clamping claw comprises at least one screw bolt, which is screwed into the cylinder head and engages through the clamping claw, wherein a nut is provided which, screwed onto the screw bolt, forces the clamping claw in the direction of the cylinder head in such a manner, that the clamping claw presses the fuel injection device against the respective seat in the cylinder head.
  • the fastening means for at least one clamping claw comprises at least one through-head screw with a screw head which engages through the clamping claw and is screwed into the cylinder head so that the screw head urges the clamping claw in the direction of the cylinder head such that the clamping claw forces the fuel injection device against the respective one Seat in the cylinder head presses.
  • the clamping claw is formed in three parts and two clamping bracket, each forming one side of the two arms of the clamping claw, as well as a clip piece, which holds the two clamping bracket and through which engages the fastener must after maintenance or repair work on the fuel injectors after the loosening of the fasteners not the complete clamps but only the clamps are replaced.
  • the clamping bracket are formed as sheet metal stampings and / or the staple piece as a sheet metal part, casting or sintered part.
  • the invention comprises a fastening and sealing of, for example, CR (common rail) injectors in a cylinder head of an internal combustion engine.
  • CR common rail
  • a clamping claw is always provided for fastening two injectors each with a fastening screw.
  • the screw connection always takes place in the cylinder head.
  • the preload force on the injectors must be set exactly, otherwise damage to the injector or leaks may occur.
  • the system must therefore always present a minimum preload force, with which the two injectors can be safely sealed.
  • the preload force must be limited to the top so that the injectors are not destroyed.
  • an example M8 threaded bolt 12 is screwed into the cylinder head 10 between each 2 cylinders.
  • the threaded bolt 12 is screwed in to the bottom of the hole.
  • a lead frame 14 is placed with liquid sealant and screwed with, for example M6 combination screws 16.
  • bearing bridges connecting webs between intake and exhaust camshaft bearing
  • the webs are fixed with, for example 2xM6 combination screws (not shown).
  • a replacement of 2xM6 combination screw by 1xM8 combination screw may be provided at these locations.
  • a cylinder head cover 20 is installed.
  • metallic support sleeves 22 are introduced (injected or hammered) in the cylinder head cover. These support sleeves 22 sit loosely on the already mounted M8 nut 18.
  • each a sealing ring 26 is mounted in the region of fuel injectors 24 and in the region of the threaded bolt 12, a seal 28 is integrated to the lead frame.
  • each 2 fuel injectors 24 are fitted together with a clamping claw 30 and inserted together through the two sealing rings 26 in the cylinder head cover 20 in the cylinder head 10.
  • the clamping claw 30 is threaded over a through hole on the threaded bolt 12.
  • the system of fuel injectors 24 and clamping claw 30 is pressed against a sealing seat 32 in an injector bore of the cylinder head 10. Subsequently, the composite is screwed to another example M8 nut 34.
  • the clamping claw 30 is bolted by the applied torque of, for example 20Nm and a further rotation angle of 90 ° to block.
  • the force flow in the region of the threaded bolt 12 thus passes through the outer M8 nut 34 through the clamping claw 30, the sleeve 22, the other M8 nut 18 and the lead frame 14 in the cylinder head 10.
  • the strength of the M8 gland is designed in such a way that it is always possible to screw to block under all tolerance conditions. This is important so that the sealing compound comprising cylinder head cover 20 and lead frame 14 works and so that it can not come to relative movements between the clamping claw 30 and the fuel injectors 24 and between the clamping claw 30 and the sleeve 22.
  • the tolerances are set on the side of the fuel injectors 24 from the height tolerances of the bearing surfaces of the clamping claw 30 to the fuel injectors 24 and amount to up to 1.1 mm. In the area of the support of the clamping claw 30 on the sleeve 22, the tolerances of clamping claw 30, sleeve 22, lead frame 14 and cylinder head 10 together. Here also tolerances in the range of 1.2 mm can result.
  • a distance "x" between clamping claw 30 and sleeve 22 is now designed and set.
  • the case of "least strain path" of the cleat 30 to block fit is relevant. This means that the clamping claw 30 must have sufficient rigidity even with small deformation paths in order to achieve the required preload forces.
  • the clamping claw 30 is designed such that plastic deformation occurs in the clamping claw 30 and thus no further increase in preload force on the fuel injector 24 above the maximum permissible value of 9 kN per fuel injector 24 is possible.
  • the minimum deformation path is thus dependent on the tolerances of the components involved and the selected distance "x" between clamping claw 30 and sleeve 22. The distance "x" results now from the tolerances and a minimum necessary deformation of the plastic deformation of the arms of the clamping claws 30th for achieving the minimum preload force.
  • the clamping claw 30 is designed such that a plastic deformation always takes place in the arms of the clamping claw 30.
  • the middle region of the clamping claw 30 with the through hole and the nut pad up and the sleeve pad down are kept very stiff. This ensures that the support surfaces are not subject to deformation and it does not come to edge supports and biasing force losses.
  • the arms of the clamping claw 30 are designed so that all deformations take place there.
  • the cross-section of the arms is reduced in horizontal section up to the bearing surfaces of the clamping claw 30 depending on the material stiffness and the resulting bending load under load by the screwing.
  • the width of the arms is kept constant.
  • the cross section is chosen such that the minimum preload force is reliably achieved and the maximum allowable bending stress is not exceeded in the transition of the arms in resting feet. From the interplay between geometry and material properties, different variants of clamping claws 30 can now be produced. This has the advantage that one chooses stiffer materials for cramped space conditions, which manage with smaller cross-sections. With sufficient space, however, more cost-effective materials are chosen, resulting in this larger cross-sections in the arms of the clamping claw 30.
  • the distance "x" is a variable that can be used for the optimization.
  • FIGS. 2 and 3 A second, alternative embodiment is in FIGS. 2 and 3 shown. Functionally identical parts are denoted by the same reference numerals as in Fig. 1 so that their explanation to the above description of Fig. 1 is referenced.
  • Fig. 2 realized the screwing of the clamping claw 30 with a through-bolt 36 instead of the above-described bolt solution.
  • the system threaded bolt 12 with two nuts 18, 34 ( Fig. 1 ) replaced by a M8 combi screw 36.
  • a slowly hardening sealant is then preferably used, since the time until the necessary bolt force is applied is longer than in the solution described above Fig. 1 , For the tolerance situation on the screw side results in an improvement, since the M8 nut 18 is omitted for attachment of the lead frame 14.
  • the cylinder head 10 is provided in the preassembled state with attached and bolted cylinder head cover 20.
  • the lead frame 14 is bolted and sealed.
  • each 2 fuel injectors 24 are pre-assembled with a clamping claw 30 and threaded through the two injector sealing rings 26 in the cylinder head 10.
  • the fuel injectors 24 are inserted into the seat 32 in the cylinder head 10 (in FIGS. 2 and 3 not shown) pressed.
  • the fastening screw 36 is inserted through the clamping claw 30 in the cylinder head 10 and bolted with 10Nm and 90 ° further rotation.
  • the fuel injectors 24 are now mounted.
  • a stiff clamping claw 30 is used, which allows only a slight deflection
  • the power flow through the screw 36 thus goes on the one hand directly into the cylinder head 10 and on the other hand directly to the fuel injectors 24.
  • the screw 36 for example, an M6 screw, both can be designed with a washer as well as a one-piece screw.
  • the screw 36 has a sealing shank which seals the screw over the cylinder head cover 20.
  • a sealing rubber 38 is mounted in the cylinder head cover 20. This rubber seal 38 is either molded or mounted.
  • the seat of the screw 36 on the clamping claw 30 is designed such that on the clamping claw 30 has a conical contour and on the screw 36 is formed a spherical contour. Thus, a line load is applied even when tilted the clamping claw 30 or the screw 36. This ensures a uniform load distribution.
  • the clamping claw 30 is not tightened in this case to block. Under the prescribed torque and the further rotation angle, the specified strength of the screw 36 results in a resulting minimum preload force, which depends on the coefficients of friction and the strength tolerances of the screw connection.
  • the screw 36 is limited in this case in its strength and is subject to plastic deformation.
  • An advantage of this system is the reusability of the clamping claw 30. Only the screw 36 must be exchanged after a removal and reinstallation of the fuel injectors 24, for example, if a repair on the injector o.ä. necessary is.
  • Another advantage is that the assembly of the cylinder head 10 prior to assembly of the fuel injectors 24 may be more complete than in the first embodiment according to FIG Fig. 1 , Furthermore, the tolerance situation is improved because of the smaller number of components. Due to the very stiff clamping claw 30, the introduction of lateral forces in the fuel injectors 24 is greatly reduced. In the geometry of the clamping claw 30 is now mainly on maximum rigidity.
  • the clamping claw 30 is formed in three parts and comprises two clamping brackets 42, 44, each forming one side of the two arms of the clamping claw 30, and a central part, clip piece or clamping member 40 in the center of the clamping claw 30 for receiving the screw 36 and the guide the clamping bracket 42.
  • the system is loosely mounted and is held together by the screw forces or it is slightly prefixed by clamping.
  • the advantage of this system is that the clamping claw 30 can be disassembled without pulling both fuel injectors 24. For this purpose, one dismantles the clamping claw 30 apart and then only pulls out the fuel injector 24 to be repaired from the cylinder head 10. Another advantage is the more cost-effective production of the individual parts.

Description

Die Erfindung betrifft eine Brennkraftmaschine, insbesondere Dieselmotor, insbesondere eines Kraftfahrzeugs, mit wenigstens zwei Arbeitszylindern und einem die Arbeitszylinder verschließenden Zylinderkopf, in dem für jeden Arbeitszylinder eine Kraftstoffeinspritzvorrichtung angeordnet ist, wobei für je wenigstens zwei Kraftstoffeinspritzvorrichtungen eine Spannpratze mit wenigstens zwei Armen derart vorgesehen ist, dass jeweils ein Arm der Spannpratze auf eine Kraftstoffeinspritzvorrichtung wirkt und die jeweilige Kraftstoffeinspritzvorrichtung mit einer vorbestimmten Kraft gegen einen Sitz im Zylinderkopf drückt, wobei ein Befestigungsmittel vorgesehen ist, welches die Spannpratze am Zylinderkopf befestigt, gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to an internal combustion engine, in particular a diesel engine, in particular a motor vehicle, having at least two working cylinders and a cylinder head closing the working cylinder, in which a fuel injector is arranged for each working cylinder, wherein for each at least two fuel injectors a clamping claw with at least two arms is provided such in that one arm of the clamping claw acts on a fuel injection device and presses the respective fuel injection device against a seat in the cylinder head with a predetermined force, wherein a fastening means is provided, which fixes the clamping claw to the cylinder head, according to the preamble of claim 1.

Aus der EP 0 751 290 B1 ist eine Anordnung zum Festklemmen von zwei oder drei Kraftstoffeinspritzdüsen mit einer Düsenklemmeinrichtung bekannt. Hierbei weist die Düsenklemmeinrichtung Kontaktteile auf, die auf Klemmaufnahmesitzen der Kraftstoffeinspritzdüsen aufsitzen. Zwischen den Kontaktteilen weist die Düsenklemmeinrichtung ein Bolzeneinsatzloch auf, in das ein Klemmbolzen eingeführt ist, um einen Druck gegen die Kraftstoffeinspritzdüsen auszuüben und Abdichtlasten abzugeben. Die Düsersklemmeinrichtung beinhaltet ein Spiel, welches die Druckkraft auf die Kraftstoffeinspritzdüsen verringert, so dass bei einem vorbestimmten Grad an Bolzenanziehkraft eine im Wesentlichen gleiche Druckkraft auf den drei Kraftstoffeinspritzdüsen auftritt. Alternativ ist die Düsenklemmeinrichtung aus einem Federmaterial derart hergestellt, dass die Düsenklemmeinrichtung leicht gebogen wird.From the EP 0 751 290 B1 An arrangement for clamping two or three fuel injection nozzles with a nozzle clamping device is known. In this case, the nozzle clamping device has contact parts which rest on terminal receiving seats of the fuel injection nozzles. Between the contact parts, the nozzle clamping device has a bolt insertion hole into which a clamping bolt is inserted to exert a pressure against the fuel injection nozzles and deliver sealing loads. The nozzle clamp includes a clearance that reduces the pressure force on the fuel injectors such that at a predetermined degree of bolt attraction force, a substantially equal compressive force occurs on the three fuel injectors. Alternatively, the nozzle clamping device is made of a spring material such that the nozzle clamping device is slightly bent.

Der Erfindung liegt die Aufgabe zugrunde, eine Brennkraftmaschine der o.g. Art hinsichtlich Montage und Wartungsfreundlichkeit zu verbessern.The invention is based on the object, an internal combustion engine og. Improve the way of installation and ease of maintenance.

Diese Aufgabe wird erfindungsgemäß durch eine Brennkraftmaschine der o.g. Art mit den in Anspruch 1 gekennzeichneten Merkmalen gelöst. Vorteilhafte Ausgestaltungen der Erfindung sind in den weiteren Ansprüchen beschrieben.This object is achieved by an internal combustion engine o.g. Art solved with the features characterized in claim 1. Advantageous embodiments of the invention are described in the further claims.

Dazu ist es bei einer Brennkraftmaschine der o.g. Art erfindungsgemäß vorgesehen, dass die Arme der Spannpratze und/oder das Befestigungsmittel derart ausgebildet ist bzw. sind, dass oberhalb der vorbestimmten Kraft für den Andruck der Kraftstoffeinspritzvorrichtungen gegen den jeweiligen Sitz im Zylinderkopf die Arme der Spannpratze und/oder das Befestigungsmittel einer plastischen Verformung unterliegen.For this purpose, it is provided according to the invention in an internal combustion engine of the type mentioned above that the arms of the clamping claw and / or the fastening means is or are such that above the predetermined force for the pressure of the fuel injectors against subject the respective seat in the cylinder head, the arms of the clamping claw and / or the fastening means of a plastic deformation.

Dies hat den Vorteil, dass auf einfache Weise eine vorbestimmte Andruckkraft der Kraftstoffeinspritzvorrichtungen gegen den jeweiligen Sitz im Zylinderkopf sichergestellt und eine Beschädigung der Kraftstoffeinspritzvorrichtungen bei der Montage durch eine zu hohe Andruckkraft wirksam vermieden ist.This has the advantage that it ensures in a simple manner a predetermined pressure force of the fuel injectors against the respective seat in the cylinder head and damage to the fuel injectors during assembly is effectively avoided by an excessive pressure force.

In einer bevorzugten Ausführungsform umfasst das Befestigungsmittel für wenigstens eine Spannpratze wenigstens einen Schraubbolzen, welcher in den Zylinderkopf eingeschraubt ist und durch die Spannpratze hindurch greift, wobei eine Schraubenmutter vorgesehen ist, welche auf den Schraubbolzen aufgeschraubt die Spannpratze in Richtung des Zylinderkopfes derart mit Kraft beaufschlagt, dass die Spannpratze die Kraftstoffeinspritzvorrichtung gegen den jeweiligen Sitz im Zylinderkopf drückt.In a preferred embodiment, the fastening means for at least one clamping claw comprises at least one screw bolt, which is screwed into the cylinder head and engages through the clamping claw, wherein a nut is provided which, screwed onto the screw bolt, forces the clamping claw in the direction of the cylinder head in such a manner, that the clamping claw presses the fuel injection device against the respective seat in the cylinder head.

Zweckmäßigerweise umfasst das Befestigungsmittel für wenigstens eine Spannpratze wenigstens eine Durchsteckschraube mit Schraubenkopf, welche durch die Spannpratze hindurch greift und in den Zylinderkopf geschraubt ist, so dass der Schraubenkopf die Spannpratze in Richtung des Zylinderkopfes derart mit Kraft beaufschlagt, dass die Spannpratze die Kraftstoffeinspritzvorrichtung gegen den jeweiligen Sitz im Zylinderkopf drückt.Expediently, the fastening means for at least one clamping claw comprises at least one through-head screw with a screw head which engages through the clamping claw and is screwed into the cylinder head so that the screw head urges the clamping claw in the direction of the cylinder head such that the clamping claw forces the fuel injection device against the respective one Seat in the cylinder head presses.

Dadurch, dass die Spannpratze dreiteilig ausgebildet ist und zwei Spannbügel, die jeweils eine Seite der beiden Arme der Spannpratze ausbilden, sowie ein Klammerstück aufweist, welches die beiden Spannbügel zusammenhält und durch welches das Befestigungsmittel greift, müssen bei Wartungs- oder Reparaturarbeiten an den Kraftstoffeinspritzvorrichtungen nach dem Lösen der Befestigungsmittel nicht die vollständigen Spannpratzen sondern nur die Spannbügel ausgetauscht werden.Characterized in that the clamping claw is formed in three parts and two clamping bracket, each forming one side of the two arms of the clamping claw, as well as a clip piece, which holds the two clamping bracket and through which engages the fastener must after maintenance or repair work on the fuel injectors after the loosening of the fasteners not the complete clamps but only the clamps are replaced.

Zweckmäßigerweise sind die Spannbügel als Blechstanzteile und/oder das Klammerstück als Blechteil, Gussteil oder Sinterteil ausgebildet.Conveniently, the clamping bracket are formed as sheet metal stampings and / or the staple piece as a sheet metal part, casting or sintered part.

Die Erfindung wird im Folgenden anhand der Zeichnung näher erläutert. Diese zeigt in

Fig. 1
eine erste bevorzugte Ausführungsform einer erfindungsgemäßen Brennkraftmaschine in Schnittansicht,
Fig. 2
eine zweite bevorzugte Ausführungsform einer erfindungsgemäßen Brennkraftmaschine in Schnittansicht und
Fig. 3
die zweite bevorzugte Ausführungsform einer erfindungsgemäßen Brennkraftmaschine gemäß Fig. 2 in Aufsicht.
The invention will be explained in more detail below with reference to the drawing. This shows in
Fig. 1
a first preferred embodiment of an internal combustion engine according to the invention in sectional view,
Fig. 2
A second preferred embodiment of an internal combustion engine according to the invention in sectional view and
Fig. 3
the second preferred embodiment of an internal combustion engine according to the invention Fig. 2 in supervision.

Die Erfindung umfasst eine Befestigung und Abdichtung von beispielsweise CR(Common-Rail)-Injektoren in einem Zylinderkopf einer Brennkraftmaschine. Erfindungsgemäß ist immer eine Spannpratze zur Befestigung von je 2 Injektoren mit einer Befestigungsschraube vorgesehen. Die Verschraubung erfolgt immer im Zylinderkopf. Hierbei muss die Vorspannkraft auf die Injektoren genau eingestellt werden, da es sonst zu Beschädigungen im Injektor oder zu Undichtigkeiten kommen kann. Das System muss also immer eine minimale Vorspannkraft darstellen, mit der die beiden Injektoren sicher abgedichtet werden können. Außerdem muss die Vorspannkraft nach oben begrenzt werden, damit die Injektoren nicht zerstört werden.The invention comprises a fastening and sealing of, for example, CR (common rail) injectors in a cylinder head of an internal combustion engine. According to the invention, a clamping claw is always provided for fastening two injectors each with a fastening screw. The screw connection always takes place in the cylinder head. Here, the preload force on the injectors must be set exactly, otherwise damage to the injector or leaks may occur. The system must therefore always present a minimum preload force, with which the two injectors can be safely sealed. In addition, the preload force must be limited to the top so that the injectors are not destroyed.

Bei der in Fig. 1 dargestellten, ersten bevorzugten Ausführungsform ist in den Zylinderkopf 10 zwischen je 2 Zylindern ein beispielsweise M8-Gewindebolzen 12 eingeschraubt. Der Gewindebolzen 12 ist bis auf den Bohrungsgrund eingeschraubt. Anschließend wird ein Leiterrahmen 14 mit Flüssigdichtmittel aufgesetzt und mit beispielsweise M6-Kombischrauben 16 verschraubt. Dabei werden Lagerbrücken (Verbindungsstege zwischen Ein- und Auslassnockenwellenlager) im Bereich der M8-Gewindebolzen 12 mit einer beispielsweise M8-Schraubmutter 18 verschraubt. An den Stegen, an denen keine Schraubbolzen vorhanden sind, werden die Stege mit beispielsweise 2xM6-Kombischrauben (nicht dargestellt) befestigt. Alternativ kann an diesen Stellen eine Substitution von 2xM6-Kombischraube durch 1xM8-Kombischraube vorgesehen sein.At the in Fig. 1 shown, the first preferred embodiment, an example M8 threaded bolt 12 is screwed into the cylinder head 10 between each 2 cylinders. The threaded bolt 12 is screwed in to the bottom of the hole. Subsequently, a lead frame 14 is placed with liquid sealant and screwed with, for example M6 combination screws 16. In this case, bearing bridges (connecting webs between intake and exhaust camshaft bearing) are screwed in the region of the M8 threaded bolt 12 with an example M8 nut 18. At the webs, where there are no bolts, the webs are fixed with, for example 2xM6 combination screws (not shown). Alternatively, a replacement of 2xM6 combination screw by 1xM8 combination screw may be provided at these locations.

Anschließend wird eine Zylinderkopfhaube 20 verbaut. Im Bereich der Gewindebolzen 12 sind in der Zylinderkopfhaube 20 metallische Stützhülsen 22 eingebracht (eingespritzt oder eingeschlagen). Diese Stützhülsen 22 sitzen lose auf der schon montierten M8-Schraubmutter 18 auf. An der Zylinderkopfhaube 20 ist im Bereich von Kraftstoffinjektoren 24 je ein Dichtring 26 montiert und im Bereich des Gewindebolzens 12 ist eine Dichtung 28 zum Leiterrahmen integriert. Anschließend werden je 2 Kraftstoffinjektoren 24 mit einer Spannpratze 30 zusammengesteckt und gemeinsam durch die beiden Dichtringe 26 in der Zylinderkopfhaube 20 in den Zylinderkopf 10 gesteckt. Die Spannpratze 30 wird über ein Durchgangsloch auf den Gewindebolzen 12 aufgefädelt. Das System aus Kraftstoffinjektoren 24 und Spannpratze 30 wird gegen einen Dichtsitz 32 in einer Injektorbohrung des Zylinderkopfes 10 gedrückt. Anschließend wird der Verbund mit einer weiteren beispielsweise M8-Schraubmutter 34 verschraubt. Die Spannpratze 30 wird durch das angelegte Drehmoment von beispielsweise 20Nm und einem Weiterdrehwinkel von 90° auf Block verschraubt. Der Kraftfluss im Bereich der Gewindebolzen 12 läuft also über die äußere M8-Schraubmutter 34 durch die Spannpratze 30, die Hülse 22, die weitere M8-Schraubmutter 18 und den Leiterrahmen 14 in den Zylinderkopf 10. Auf der Seite des Kraftstoffinjektors 24 wird die Kraft durch die M8-Schraubmutter 34 und über die beiden Arme der Spannpratze 30 auf den Kraftstoffinjektor 24 und dann auf eine Dichtscheibe des Kraftstoffinjektors 24 im Kopf geleitet.Subsequently, a cylinder head cover 20 is installed. In the area of the threaded bolt 12 20 metallic support sleeves 22 are introduced (injected or hammered) in the cylinder head cover. These support sleeves 22 sit loosely on the already mounted M8 nut 18. On the cylinder head cover 20 each a sealing ring 26 is mounted in the region of fuel injectors 24 and in the region of the threaded bolt 12, a seal 28 is integrated to the lead frame. Subsequently, each 2 fuel injectors 24 are fitted together with a clamping claw 30 and inserted together through the two sealing rings 26 in the cylinder head cover 20 in the cylinder head 10. The clamping claw 30 is threaded over a through hole on the threaded bolt 12. The system of fuel injectors 24 and clamping claw 30 is pressed against a sealing seat 32 in an injector bore of the cylinder head 10. Subsequently, the composite is screwed to another example M8 nut 34. The clamping claw 30 is bolted by the applied torque of, for example 20Nm and a further rotation angle of 90 ° to block. The force flow in the region of the threaded bolt 12 thus passes through the outer M8 nut 34 through the clamping claw 30, the sleeve 22, the other M8 nut 18 and the lead frame 14 in the cylinder head 10. On the side of the fuel injector 24, the force through the M8 nut 34 and the two arms of the clamping claw 30 on the fuel injector 24 and then on a Sealing disk of the fuel injector 24 passed in the head.

Durch das Verschrauben der Spannpratze 30 auf Block wird auch die notwendige Anpresskraft für die Dichtung 28 in der Zylinderkopfhaube 20 auf den Leiterrahmen 14 im Bereich der Gewindebolzen 12 aufgebracht.By screwing the clamping claw 30 to block and the necessary contact pressure for the seal 28 in the cylinder head cover 20 is applied to the lead frame 14 in the region of the threaded bolt 12.

Die Festigkeit der M8-Verschraubung ist derart ausgelegt, dass unter allen Toleranzbedingungen immer eine Verschraubung auf Block möglich ist. Dies ist wichtig, damit der Dichtverbund umfassend Zylinderkopfhaube 20 und Leiterrahmen 14 funktioniert und damit es nicht zu Relativbewegungen zwischen der Spannpratze 30 und den Kraftstoffinjektoren 24 sowie zwischen der Spannpratze 30 und der Hülse 22 kommen kann. Die Toleranzen setzen sich auf der Seite der Kraftstoffinjektoren 24 aus den Höhentoleranzen der Auflageflächen der Spannpratze 30 an den Kraftstoffinjektoren 24 zusammen und betragen bis zu 1,1 mm. Im Bereich der Auflage der Spannpratze 30 auf der Hülse 22 setzten sich die Toleranzen aus Spannpratze 30, Hülse 22, Leiterrahmen 14 und Zylinderkopf 10 zusammen. Hier können sich ebenfalls Toleranzen im Bereich von 1,2 mm ergeben. Als minimaler Verformungsweg wird nun ein Abstand "x" zwischen Spannpratze 30 und Hülse 22 ausgelegt und eingestellt.The strength of the M8 gland is designed in such a way that it is always possible to screw to block under all tolerance conditions. This is important so that the sealing compound comprising cylinder head cover 20 and lead frame 14 works and so that it can not come to relative movements between the clamping claw 30 and the fuel injectors 24 and between the clamping claw 30 and the sleeve 22. The tolerances are set on the side of the fuel injectors 24 from the height tolerances of the bearing surfaces of the clamping claw 30 to the fuel injectors 24 and amount to up to 1.1 mm. In the area of the support of the clamping claw 30 on the sleeve 22, the tolerances of clamping claw 30, sleeve 22, lead frame 14 and cylinder head 10 together. Here also tolerances in the range of 1.2 mm can result. As a minimum deformation path, a distance "x" between clamping claw 30 and sleeve 22 is now designed and set.

Für eine minimale Vorspannkraft von beispielsweise 7kN ist der Fall "kleinster Verformungsweg" der Spannpratze 30 bis zum Blocksitz relevant. Das bedeutet, dass die Spannpratze 30 schon bei kleinen Verformungswegen eine ausreichende Steifigkeit haben muss, um die geforderten Vorspannkräfte zu erreichen. Bei "großen Verformungswegen" bis zum Blocksitz bei entgegengesetzter Toleranzlage ist die Spannpratze 30 derart ausgelegt, dass es zu einer plastischen Verformung in der Spannpratze 30 kommt und somit kein weiterer Zuwachs an Vorspannkraft auf den Kraftstoffinjektor 24 oberhalb des maximal zulässigen Wertes von 9kN pro Kraftstoffinjektor 24 möglich ist. Der minimale Verformungsweg ist also abhängig von den Toleranzen der beteiligten Bauteile und dem gewählten Abstand "x" zwischen Spannpratze 30 und Hülse 22. Der Abstand "x" ergibt sich nun aus den Toleranzen und einem minimal notwendigen Verformungsweg der plastischen Verformung der Arme der Spannpratzen 30 für das Erreichen der minimalen Vorspannkraft.For a minimum preload force of, for example, 7kN, the case of "least strain path" of the cleat 30 to block fit is relevant. This means that the clamping claw 30 must have sufficient rigidity even with small deformation paths in order to achieve the required preload forces. In the case of "large deformation paths" until the block seat is in the opposite tolerance position, the clamping claw 30 is designed such that plastic deformation occurs in the clamping claw 30 and thus no further increase in preload force on the fuel injector 24 above the maximum permissible value of 9 kN per fuel injector 24 is possible. The minimum deformation path is thus dependent on the tolerances of the components involved and the selected distance "x" between clamping claw 30 and sleeve 22. The distance "x" results now from the tolerances and a minimum necessary deformation of the plastic deformation of the arms of the clamping claws 30th for achieving the minimum preload force.

Da die zulässigen Kräfte auf die Kraftstoffinjektoren 24 bekannt sind, ist eine Kombination aus Pratzengeometrie, Materialeigenschaften und Abstand "x" als Lösungsweg vorgesehen. Die Spannpratze 30 ist derart ausgelegt, dass eine plastische Verformung immer in den Armen der Spannpratze 30 erfolgt. Der mittlere Bereich der Spannpratze 30 mit der Durchgangsbohrung und der Mutternauflage oben und der Hülsenauflage unten sind sehr steif gehalten. Dadurch ist sichergestellt, dass die Auflageflächen keiner Verformung unterworfen sind und es so nicht zu Kantenträgern und Vorspannkraftverlusten kommt.Since the permissible forces on the fuel injectors 24 are known, a combination of gripper geometry, material properties and distance "x" is provided as a solution. The clamping claw 30 is designed such that a plastic deformation always takes place in the arms of the clamping claw 30. The middle region of the clamping claw 30 with the through hole and the nut pad up and the sleeve pad down are kept very stiff. This ensures that the support surfaces are not subject to deformation and it does not come to edge supports and biasing force losses.

Die Arme der Spannpratze 30 sind derart ausgelegt, dass sämtliche Verformungen dort stattfinden. Der Querschnitt der Arme verringert sich im Horizontalschnitt bis zu den Auflageflächen der Spannpratze 30 in Abhängigkeit von der Materialsteifigkeit und der daraus resultierenden Biegebelastung bei anliegender Last durch den Schraubfall. Die Breite der Arme ist konstant gehalten. Hierbei ist der Querschnitt derart gewählt, dass die minimale Vorspannkraft sicher erreicht wird und die maximal zulässige Biegespannung beim Übergang der Arme in aufliegende Füßchen nicht überschritten wird. Aus dem Zusammenspiel zwischen Geometrie und Materialeigenschaften lassen sich nun unterschiedliche Varianten von Spannpratzen 30 erzeugen. Das hat den Vorteil, dass man für beengte Platzverhältnisse steifere Materialien wählt, die mit geringeren Querschnitten auskommen. Bei genügend Bauraum hingegen werden kostengünstigere Materialien gewählt, wobei sich hierbei größere Querschnitte in den Armen der Spannpratze 30 ergeben. Der Abstand "x" ist eine Variable, die zur Optimierung herangezogen werden kann.The arms of the clamping claw 30 are designed so that all deformations take place there. The cross-section of the arms is reduced in horizontal section up to the bearing surfaces of the clamping claw 30 depending on the material stiffness and the resulting bending load under load by the screwing. The width of the arms is kept constant. Here, the cross section is chosen such that the minimum preload force is reliably achieved and the maximum allowable bending stress is not exceeded in the transition of the arms in resting feet. From the interplay between geometry and material properties, different variants of clamping claws 30 can now be produced. This has the advantage that one chooses stiffer materials for cramped space conditions, which manage with smaller cross-sections. With sufficient space, however, more cost-effective materials are chosen, resulting in this larger cross-sections in the arms of the clamping claw 30. The distance "x" is a variable that can be used for the optimization.

Eine zweite, alternative Ausführungsform ist in Fig. 2 und 3 dargestellt. Funktionsgleiche Teile sind mit gleichen Bezugszeichen bezeichnet, wie in Fig. 1, so dass zu deren Erläuterung auf die obige Beschreibung der Fig. 1 verwiesen wird. Im Unterschied zur ersten Ausführungsform gemäß Fig. 1 ist bei der zweiten Ausführungsform gemäß Fig. 2 die Verschraubung der Spannpratze 30 mit einer Durchsteckschraube 36 anstelle der oben beschriebenen Bolzenlösung realisiert. Hierbei wird das System Gewindebolzen 12 mit zwei Schraubmuttern 18, 34 (Fig. 1) durch eine M8-Kombischraube 36 ersetzt. Für die Verschraubung der Spannpratze 30 und deren Kraftbeaufschlagen bei den Kraftstoffinjektoren 24 ergeben sich keine weiteren Auswirkungen. Für die Abdichtung des Leiterrahmens 14 zum Zylinderkopf 10 wird dann bevorzugt ein langsam aushärtendes Dichtmittel verwendet, da die Zeit, bis die notwendige Schraubenkraft anliegt, länger ist als in der oben beschriebenen Lösung gemäß Fig. 1. Für die Toleranzsituation auf der Schraubenseite ergibt sich eine Verbesserung, da die M8-Schraubutter 18 zur Befestigung der Leiterrahmens 14 entfällt.A second, alternative embodiment is in FIGS. 2 and 3 shown. Functionally identical parts are denoted by the same reference numerals as in Fig. 1 so that their explanation to the above description of Fig. 1 is referenced. Unlike the first embodiment according to Fig. 1 is according to the second embodiment Fig. 2 realized the screwing of the clamping claw 30 with a through-bolt 36 instead of the above-described bolt solution. In this case, the system threaded bolt 12 with two nuts 18, 34 ( Fig. 1 ) replaced by a M8 combi screw 36. For the screwing of the clamping claw 30 and the application of force to the fuel injectors 24 there are no further effects. For the sealing of the lead frame 14 to the cylinder head 10, a slowly hardening sealant is then preferably used, since the time until the necessary bolt force is applied is longer than in the solution described above Fig. 1 , For the tolerance situation on the screw side results in an improvement, since the M8 nut 18 is omitted for attachment of the lead frame 14.

Nachfolgend wird der Zusammenbau der zweiten bevorzugten Ausführungsform gemäß Fig. 2 beschrieben. Der Zylinderkopf 10 wird in vormontierten Zustand mit aufgesetzter und verschraubter Zylinderkopfhaube 20 bereitgestellt. Der Leiterrahmen 14 ist verschraubt und abgedichtet. Nun werden je 2 Kraftstoffinjektoren 24 mit einer Spannpratze 30 vormontiert und durch die beiden Injektordichtringe 26 in den Zylinderkopf 10 eingefädelt. Dann werden die Kraftstoffinjektoren 24 in den Sitz 32 im Zylinderkopf 10 (in Fig. 2 und 3 nicht dargestellt) gedrückt. Die Befestigungsschraube 36 wird durch die Spannpratze 30 in den Zylinderkopf 10 gesteckt und mit 10Nm und 90° Weiterdrehwinkel verschraubt. Die Kraftstoffinjektoren 24 sind nun montiert.Hereinafter, the assembly of the second preferred embodiment according to Fig. 2 described. The cylinder head 10 is provided in the preassembled state with attached and bolted cylinder head cover 20. The lead frame 14 is bolted and sealed. Now each 2 fuel injectors 24 are pre-assembled with a clamping claw 30 and threaded through the two injector sealing rings 26 in the cylinder head 10. Then, the fuel injectors 24 are inserted into the seat 32 in the cylinder head 10 (in FIG FIGS. 2 and 3 not shown) pressed. The fastening screw 36 is inserted through the clamping claw 30 in the cylinder head 10 and bolted with 10Nm and 90 ° further rotation. The fuel injectors 24 are now mounted.

Bei diesem System wird eine steife Spannpratze 30 eingesetzt, die nur eine geringe Durchbiegung zulässt Der Kraftfluss über die Schraube 36 geht also einerseits direkt in den Zylinderkopf 10 und andererseits direkt auf die Kraftstoffinjektoren 24. Die Schraube 36 ist beispielsweise eine M6-Schraube, die sowohl mit Unterlegscheibe als auch als einteilige Schraube ausgeführt sein kann.In this system, a stiff clamping claw 30 is used, which allows only a slight deflection The power flow through the screw 36 thus goes on the one hand directly into the cylinder head 10 and on the other hand directly to the fuel injectors 24. The screw 36, for example, an M6 screw, both can be designed with a washer as well as a one-piece screw.

Die Schraube 36 weist einen Dichtschaft auf, der die Schraube über die Zylinderkopfhaube 20 abdichtet. Dazu ist in der Zylinderkopfhaube 20 ein Dichtgummi 38 montiert. Dieser Dichtgummi 38 ist entweder angespritzt oder montiert. Der Sitz der Schraube 36 auf der Spannpratze 30 ist derart ausgeführt, dass auf der Spannpratze 30 eine kegelförmige Kontur und auf der Schraube 36 eine kugelförmige Kontur ausgebildet ist. Somit wird auch bei Schrägstellung der Spannpratze 30 oder der Schraube 36 eine Linienlast aufgetragen. Damit ist eine gleichmäßige Lastverteilung sichergestellt.The screw 36 has a sealing shank which seals the screw over the cylinder head cover 20. For this purpose, a sealing rubber 38 is mounted in the cylinder head cover 20. This rubber seal 38 is either molded or mounted. The seat of the screw 36 on the clamping claw 30 is designed such that on the clamping claw 30 has a conical contour and on the screw 36 is formed a spherical contour. Thus, a line load is applied even when tilted the clamping claw 30 or the screw 36. This ensures a uniform load distribution.

Die Spannpratze 30 wird in diesem Fall nicht auf Block angezogen. Unter dem vorgeschriebenen Drehmoment und dem Weiterdrehwinkel ergibt sich aus der festgelegten Festigkeit der Schraube 36 eine resultierende minimale Vorspannkraft, die von den Reibbeiwerten und den Festigkeitstoleranzen der Schraubenverbindung abhängig ist. Die Schraube 36 ist für diesen Fall in ihrer Festigkeit eingeschränkt und unterliegt einer plastischen Verformung. Ein Vorteil dieses Systems ist die Wiederverwendbarkeit der Spannpratze 30. Lediglich die Schraube 36 muss nach einem Aus- und wieder Einbau der Kraftstoffinjektoren 24 getauscht werden, beispielsweise wenn eine Reparatur am Injektor o.ä. notwendig ist. Ein weiterer Vorteil liegt darin, dass der Zusammenbau des Zylinderkopfes 10 vor der Montage der Kraftstoffinjektoren 24 vollständiger sein kann als bei der ersten Ausführungsform gemäß Fig. 1. Weiterhin ist die Toleranzsituation wegen der geringeren Anzahl der Bauteile verbessert. Durch die sehr steife Spannpratze 30 wird die Einleitung von Querkräften in die Kraftstöffinjektoren 24 stark reduziert. Bei der Geometriegebung der Spannpratze 30 kommt es nun hauptsächlich auf maximale Steifigkeit an.The clamping claw 30 is not tightened in this case to block. Under the prescribed torque and the further rotation angle, the specified strength of the screw 36 results in a resulting minimum preload force, which depends on the coefficients of friction and the strength tolerances of the screw connection. The screw 36 is limited in this case in its strength and is subject to plastic deformation. An advantage of this system is the reusability of the clamping claw 30. Only the screw 36 must be exchanged after a removal and reinstallation of the fuel injectors 24, for example, if a repair on the injector o.ä. necessary is. Another advantage is that the assembly of the cylinder head 10 prior to assembly of the fuel injectors 24 may be more complete than in the first embodiment according to FIG Fig. 1 , Furthermore, the tolerance situation is improved because of the smaller number of components. Due to the very stiff clamping claw 30, the introduction of lateral forces in the fuel injectors 24 is greatly reduced. In the geometry of the clamping claw 30 is now mainly on maximum rigidity.

Aus Fig. 3 ist zusätzlich eine besondere Ausführungsform der Spannpratze 30 ersichtlich. Unabhängig vom Verschraubungskonzept gemäß Fig. 1 oder Fig. 2 ist die Spannpratze 30 beispielsweise dreiteilig ausgebildet und umfasst zwei Spannbügel 42, 44, die jeweils eine Seite der beiden Arme der Spannpratze 30 ausbilden, und ein Zentralteil, Klammerstück oder Klemmteil 40 in der Mitte der Spannpratze 30 zur Aufnahmen der Schraube 36 und zur Führung der Spannbügel 42. Das System ist lose montiert und wird durch die Schraubenkräfte zusammengehalten oder es ist durch Klemmen leicht vorfixiert. Der Vorteil dieses Systems liegt darin, dass die Spannpratze 30 ohne Ziehen beider Kraftstoffinjektoren 24 demontiert werden kann. Hierzu baut man die Spannpratze 30 auseinander und zieht dann nur den zu reparierenden Kraftstoffnjektor 24 aus dem Zylinderkopf 10 heraus. Ein weiter Vorteil ist die kostengünstigere Herstellung der Einzelteile.Out Fig. 3 In addition, a particular embodiment of the clamping claw 30 can be seen. Regardless of the bolting concept according to Fig. 1 or Fig. 2 For example, the clamping claw 30 is formed in three parts and comprises two clamping brackets 42, 44, each forming one side of the two arms of the clamping claw 30, and a central part, clip piece or clamping member 40 in the center of the clamping claw 30 for receiving the screw 36 and the guide the clamping bracket 42. The system is loosely mounted and is held together by the screw forces or it is slightly prefixed by clamping. The advantage of this system is that the clamping claw 30 can be disassembled without pulling both fuel injectors 24. For this purpose, one dismantles the clamping claw 30 apart and then only pulls out the fuel injector 24 to be repaired from the cylinder head 10. Another advantage is the more cost-effective production of the individual parts.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

1010
Zylinderkopfcylinder head
1212
Gewindebolzenthreaded bolt
1414
Leiterrahmenleadframe
1616
M6-KombischraubenM6 combination screws
1818
Schraubmutternut
2020
ZylinderkopfhaubeCylinder head cover
2222
metallische Stützhülsenmetallic support sleeves
2424
Kraftstoffinjektorfuel injector
2626
Dichtringseal
2828
Dichtung zum LeiterrahmenSeal to the lead frame
3030
Spannpratzeclamping shoe
3232
Dichtsitzsealing seat
3434
Schraubmutternut
3636
DurchsteckschraubeThrough bolt
3838
Dichtgummirubber seal
4040
Klemmteilclamping part
4242
Spannbügeltensioning bow
4444
Spannbügeltensioning bow

Claims (6)

  1. Internal combustion engine, in particular diesel engine, in particular of a motor vehicle, having at least two working cylinders and having a cylinder head (10) which closes off the working cylinders and in which there is arranged one fuel injection device (24) for each working cylinder, wherein, for in each case at least two fuel injection devices (24), one clamping claw (30) with at least two arms is provided such that in each case one arm of the clamping claw (30) acts on one fuel injection device (24) and pushes the respective fuel injection device (24) with a predetermined force against a seat (32) in the cylinder head (10), wherein a fastening means (12; 36) is provided which fastens the clamping claw (30) to the cylinder head (10), characterized in that the arms of the clamping claw (30) and/or the fastening means (12; 36) are/is designed such that, above the predetermined force for the pressing of the fuel injection devices (24) against the respective seat (32) in the cylinder head (10), the arms of the clamping claw (30) and/or the fastening means (12; 36) undergo a plastic deformation.
  2. Internal combustion engine according to Claim 1, characterized in that the fastening means for at least one clamping claw (30) comprises at least one threaded bolt (12) which is screwed into the cylinder head (10) and which extends through the clamping claw (30), wherein a threaded nut (34) is provided which, screwed onto the threaded bolt (12), acts on the clamping claw (30) with a force in the direction of the cylinder head (10) such that the clamping claw (30) pushes the fuel injection devices (24) against the respective seat (32) in the cylinder head (10).
  3. Internal combustion engine according to at least one of the preceding claims, characterized in that the fastening means comprises, for at least one clamping claw (30), at least one through-bolt (36) with bolt head, which through-bolt extends through the clamping claw (30) and is screwed into the cylinder head (10) such that the screw head acts on the clamping claw (30) with a force in the direction of the cylinder head (10) such that the clamping claw (30) pushes the fuel injection devices (24) against the respective seat (32) in the cylinder head.
  4. Internal combustion engine according to at least one of the preceding claims, characterized in that the clamping claw (30) is formed in three parts and has two clamping bows (42, 44), which form in each case one side of the two arms of the clamping claw (30), and has a clamp piece (40), which holds the two clamping bows (42, 44) together and through which the fastening means (12; 36) engages.
  5. Internal combustion engine according to Claim 4, characterized in that the clamping bows (42, 44) are in the form of sheet-metal punched parts.
  6. Internal combustion engine according to Claim 4 or 5, characterized in that the clamp piece (40) is formed as a sheet-metal part, cast part or sintered part.
EP08017534.2A 2007-10-23 2008-10-07 Combustion engine with fuel injectors Active EP2053235B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200710050512 DE102007050512A1 (en) 2007-10-23 2007-10-23 Internal combustion engine with fuel injectors

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EP2053235A2 EP2053235A2 (en) 2009-04-29
EP2053235A3 EP2053235A3 (en) 2009-11-04
EP2053235B1 true EP2053235B1 (en) 2016-12-14

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Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008009385A1 (en) 2008-02-14 2009-08-27 Volkswagen Ag Internal-combustion engine has actuator and actuator locking cylinder head, in which fuel injection devices are arranged for each actuator, and fastening elements are provided for attachment of tensioning bracket at cylinder head
GB2546500B (en) 2016-01-19 2019-07-24 Perkins Engines Co Ltd Reversible injector clamp
DE102020004625A1 (en) 2020-07-30 2022-02-03 Deutz Aktiengesellschaft injector spillage

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB8728518D0 (en) * 1987-12-05 1988-01-13 Lucas Ind Plc Clamping arrangement
JP2937081B2 (en) * 1995-06-26 1999-08-23 いすゞ自動車株式会社 Fuel injection nozzle tightening device
FR2763379B1 (en) * 1997-05-16 1999-07-16 Renault INJECTOR FIXING FLANGE
DE10155678A1 (en) * 2001-11-13 2003-05-22 Bosch Gmbh Robert Clamp, to lock a fuel injection valve in its drilling through the cylinder head of an IC motor, has a clamp paw which presses symmetrically against a linear bearing surface without a tilting movement
FR2884876B1 (en) * 2005-04-22 2007-08-03 Peugeot Citroen Automobiles Sa FIXING DEVICE FOR MOUNTING AN INJECTOR HOLDER ON AN INTERNAL COMBUSTION ENGINE AND INTERNAL COMBUSTION ENGINE COMPRISING SUCH A DEVICE

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EP2053235A3 (en) 2009-11-04

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