EP0279267B1 - Valve control device - Google Patents

Valve control device Download PDF

Info

Publication number
EP0279267B1
EP0279267B1 EP19880101417 EP88101417A EP0279267B1 EP 0279267 B1 EP0279267 B1 EP 0279267B1 EP 19880101417 EP19880101417 EP 19880101417 EP 88101417 A EP88101417 A EP 88101417A EP 0279267 B1 EP0279267 B1 EP 0279267B1
Authority
EP
European Patent Office
Prior art keywords
piston
valve
control device
housing
valve 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.)
Expired - Lifetime
Application number
EP19880101417
Other languages
German (de)
French (fr)
Other versions
EP0279267A1 (en
Inventor
Michael Dipl.-Ing. Zipprath
Dieter Schmidt
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.)
INA Waelzlager Schaeffler OHG
Original Assignee
INA Waelzlager Schaeffler OHG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by INA Waelzlager Schaeffler OHG filed Critical INA Waelzlager Schaeffler OHG
Publication of EP0279267A1 publication Critical patent/EP0279267A1/en
Application granted granted Critical
Publication of EP0279267B1 publication Critical patent/EP0279267B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/245—Hydraulic tappets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F02M59/468—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means using piezoelectric operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7771—Bi-directional flow valves
    • Y10T137/7772—One head and seat carried by head of another
    • Y10T137/7774—Supporting valve spring carried by supporting valve

Definitions

  • the invention relates to a control device with a valve, which is arranged via its inlet bore on a fuel injection line of an internal combustion engine and with its outlet line on the intake side of the injection pump, and the valve body of which is displaced by a drive member to a valve seat.
  • the drive element emits a force-displacement pulse.
  • the valve which is located in a fuel return line, is closed.
  • a desired high injection pressure builds up on the injection nozzle of the relevant cylinder of the internal combustion engine.
  • the valve body is cylindrical here and has a shaft section which consists of a resilient material, for example a polymeric material, while the tip of the valve body is a steel part. This arrangement is intended to prevent valve shocks.
  • the valve body is thus designed as a damping element. However, due to its resilient material, it cannot always guarantee an exact closing of the valve.
  • the object of the invention is to propose a control device of the type mentioned at the outset, which is separate from the fuel area, the valve always having an exact opening and closing behavior even when the length of the device components changes thermally.
  • a clearance compensation element is arranged between the valve body and the drive member, which has two pistons guided in a housing, the first piston being acted upon by the drive member, the second piston acting on the valve body and between the pistons an oil-filled pressure chamber is formed in the housing, in which there is a pressure spring acting on the pistons, and the pressure chamber is open to an oil storage space, which is sealed off from the valve, via leakage gaps existing between the pistons and their guides in the housing.
  • the compression spring presses the first piston against the drive member without play and the second piston against the valve body in the open position.
  • the drive member presses on the first piston.
  • the second piston which acts on the valve body in such a way that the valve closes, is moved over the oil filling.
  • the oil filling ensures high rigidity of the drive.
  • it is favorable that the oil filling of the pressure chamber can be selected independently of the fuel according to the necessary properties with regard to viscosity and temperature behavior.
  • the pistons have a low mass compared to the housing. This improves the dynamic properties of the overall system.
  • a check valve is arranged in the housing between the oil reservoir and the pressure chamber oil enters the pressure chamber when the pressure is released. This ensures that the pressure chamber remains oil-filled despite oil losses through the leakage gaps.
  • FIG. 1 shows a compensating element arranged on a valve in partial section.
  • a valve body (2) is slidably mounted in a valve housing (1).
  • a valve seat (3) is formed between the valve body (2) and the valve housing (1). The figure shows the valve body (2) in its open position, in which it is pressed against a stop ring (5) by means of a compression spring (4).
  • the valve seat (3) forms a liquid passage.
  • the stroke of the valve body (2) is less than 1 mm.
  • the valve body (2) has a cylindrical guide surface (6), the diameter of which is approximately the same as the diameter of the valve seat (3).
  • a circumferential recess (7) is formed on the valve body (2) between the guide surface (6) and the valve seat (3) and is open to an annular channel (8) of the valve housing (1).
  • a bore (9) opens into the annular channel (8).
  • An outlet (10) is provided on the side of the valve seat (3) facing away from the annular channel (8).
  • the bore (9) is connected to a fuel injection line leading from an injection pump to the injection nozzle of a cylinder of an internal combustion engine.
  • the outlet (10) leads back to the suction side of the injection pump.
  • the valve body (2) has a pressure compensation bore (12) that is open to the interior (11) of the stop ring (5). Fuel can collect in the interior (11).
  • a housing (13) of a compensating element (14) is attached to the stop ring (5) opposite the valve housing (1).
  • a first piston (15) is guided in the housing (13).
  • a non-return valve (16) consisting of a retaining cap (17) and a valve ball (19) which is supported thereon by a closing spring (18), is arranged on this.
  • the valve ball (19) has a ball seat (20) associated with a cavity (21) in the first piston (15).
  • a second piston (22) is also made, which consists of solid material and is formed by a ground needle, as is known from needle bearings.
  • An oil-filled pressure chamber (23) is formed between the first piston (15) and the second piston (22).
  • a pressure spring (24) is arranged in the pressure chamber (23) and is supported on the one hand by the edge of the retaining cap (17) on the first piston (15) and on the other hand by an intermediate plate (25) on the second piston (22).
  • the diameter of the first piston (15) is larger than the diameter of the second piston (22).
  • the leak gap (26) is open to an annular space (28) which is connected to the cavity (21) via a passage (29).
  • the leakage gap (27) is open to an annular space (30) which is connected to the through at least one bore (31) Annulus (28) is connected.
  • the cavity (21), the annular spaces (28,30) and the bore (31) together form an oil-filled oil storage space.
  • the pistons (15, 22) are designed to be as long as possible in relation to the available installation space.
  • the length of the second piston (22) is greater than its diameter.
  • the annular space (30) is sealed off from the interior (11) by means of a membrane arrangement (32).
  • the membrane arrangement (32) has a plate (33) which lies between the second piston (22) and the valve body (2).
  • the plate (33) is provided on its circumference with a groove (34) which is partially circular in cross section.
  • An elastic ring (36) made of rubber is vulcanized to the groove (34) and its edges (35). A comparatively large connecting area between the plate (33) and the ring (36) is achieved.
  • the elastic ring (36) is vulcanized on its outer circumference to a sleeve (37). This sits in a press fit in a bore (38) of the housing (13).
  • the annular space (28) is sealed off from the environment with a similar membrane arrangement (39).
  • the membrane arrangement (39) has a plate (40) with a groove (41) which is semicircular in cross section.
  • An elastic ring (43) made of rubber is vulcanized to these and their edges (42).
  • the outer circumference of the ring (43) is vulcanized to a sleeve (44) which is press-fitted into a bore (45) in the housing (13).
  • the plate (40) is provided with a filling opening (46) for oil, which is closed with a stopper (47).
  • the plate (40) abuts the first piston (15). On its side facing away from this lies the drive member, not shown.
  • the elastic rings (36, 43) can also be formed from plastic parts or sheet metal parts.
  • the injection pump pumps fuel through the bore (9), the annular channel (8), the peripheral recess (7), the valve seat (3) and the outlet (10).
  • the associated injector is closed.
  • the compression spring (4) keeps the valve seat (3) open.
  • the pressure chamber (23) and the oil reservoir are filled with oil.
  • the first piston (15) is free of play via the plate (40) to the drive member and the second piston (22) is free of play via the plate (33) pressed against the valve body (2).
  • the drive member If the drive member is now actuated, it moves the first piston (15) over the plate (40). This displaces the oil in the pressure chamber (23). As a result, the second piston (22) is displaced in accordance with the translation. He presses against the force of the compression spring (4) on the plate (33) so that the valve seat (3) closes. As a result, the desired pressure builds up in the ring channel (8) and thus also at the injection nozzle.
  • the locking force to be transmitted for the valve seat (3) via the first piston (15), the oil filling of the pressure chamber (23) and the second piston (22) is comparatively low, since the diameter of the valve seat (3) on the one hand of the ring channel (8) and the diameter of the guide surface (6) on the other hand of the ring channel (8) are substantially the same size.
  • valve body (2) As long as the valve body (2) is kept in the closed position is, oil leaks from the pressure chamber (23) into the annular spaces (28, 30) via the leakage gaps (26, 27). However, the closed position of the valve seat (3) is maintained.
  • the compression spring (4) can push back the second piston (22) and thereby the first piston (15) with the plate (40) via the plate (33).
  • the plate (40) remains in contact with the drive member.
  • the compression spring (24) can relax further, which is associated with an increase in volume of the pressure chamber (23). This creates a negative pressure in relation to the oil reservoir.
  • the valve ball (19) lifts off the ball seat (20) so that oil is refilled into the pressure chamber (23).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

Die Erfindung betrifft eine Steuereinrichtung mit einem Ventil, das über seine Einlaß-Bohrung an einer Kraftstoff-Einspritzleitung eines Verbrennungsmotors und mit seiner Auslaß-Leitung an der Ansaugseite der Einspritzpumpe angeordnet ist, und dessen Ventilkörper von einem Antriebsglied an einen Ventilsitz verschoben wird.The invention relates to a control device with a valve, which is arranged via its inlet bore on a fuel injection line of an internal combustion engine and with its outlet line on the intake side of the injection pump, and the valve body of which is displaced by a drive member to a valve seat.

Bei einer derartigen, aus dem Dokument US-A-4 497 298 bekannten Steuereinrichtung gibt das Antriebsglied einen Kraft-Weg-Impuls ab. Mit diesem Impuls wird das Ventil, das in einer Kraftstoff-Rückführungsleitung liegt, geschlossen. Dadurch baut sich an der Einspritzdüse des betreffenden Zylinders des Verbrennungsmotors ein gewünschter hoher Einspritzdruck auf. Der Ventilkörper ist hier zylindrisch ausgebildet und weist einen Schaftabschnitt auf, der aus einem nachgiebigen Material, beispielsweise einem polymeren Werkstoff besteht, während die Spitze des Ventilkörpers ein Stahlteil ist. Durch diese Anordnung sollen Ventilstöße verhindert werden. Der Ventilkörper ist hier also als Dämpfungselement ausgebildet. Wegen seines nachgiebigen Werkstoffs kann er jedoch nicht immer ein exaktes Schließen des Ventils gewährleisten.In such a control device known from document US-A-4 497 298, the drive element emits a force-displacement pulse. With this pulse, the valve, which is located in a fuel return line, is closed. As a result, a desired high injection pressure builds up on the injection nozzle of the relevant cylinder of the internal combustion engine. The valve body is cylindrical here and has a shaft section which consists of a resilient material, for example a polymeric material, while the tip of the valve body is a steel part. This arrangement is intended to prevent valve shocks. The valve body is thus designed as a damping element. However, due to its resilient material, it cannot always guarantee an exact closing of the valve.

Aus dem Dokument DE-C-256 641 ist eine Nockensteuerung mit hydraulischer Kraftübertragung bekannt, die nicht auf ein Ventil einwirkt, welches in einer Kraftstoff-Einspritzleitung angeordnet ist, sondern die auf ein Ein- oder Auslaßventil des Verbrennungsmotors unmittelbar einwirkt. Bei dieser hydraulischen Steuerung ist das Gestänge für den Anhub des Ventils ganz oder nahezur starr, kann sich aber nach der Anhubbewegung durch Entweichenlassen von Flüssigkeit verkürzen und nach der Schließbewegung durch Wiedereinsaugen von Flüssigkeit auf die frühere Länge wieder einstellen. Einen Hinweis auf thermisch bedingte Abmessungsänderungen enthält dieses Dokument nicht. Ein solcher ist für ein hydraulisches Ventilbetätigungselement in dem Dokument US-A-3 495 577 enthalten.From document DE-C-256 641 a cam control with hydraulic power transmission is known which does not act on a valve which is arranged in a fuel injection line, but which acts directly on an intake or exhaust valve of the internal combustion engine. In this hydraulic control, the linkage for lifting the valve is completely or almost rigid, but can shorten after the lifting movement by allowing liquid to escape and after Adjust the closing movement to the previous length by sucking in liquid again. This document does not contain any indication of thermal changes in dimensions. One such is included for a hydraulic valve actuator in document US-A-3 495 577.

Der Erfindung liegt die Aufgabe zugrunde, eine Steuereinrichtung der eingangs genannten Art vorzuschlagen, die von dem Kraftstoffbereich getrennt ist, wobei das Ventil auch bei thermisch bedingten Längenänderungen der Einrichtungsbauteile stets ein exaktes Öffnungs- und Schließverhalten aufweist.The object of the invention is to propose a control device of the type mentioned at the outset, which is separate from the fuel area, the valve always having an exact opening and closing behavior even when the length of the device components changes thermally.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß zwischen dem Ventilkörper und dem Antriebsglied ein Spiel-Ausgleichselement angeordnet ist, welches zwei in einem Gehäuse geführte Kolben aufweist, wobei der erste Kolben von dem Antriebsglied beaufschlagt ist, der zweite Kolben den Ventilkörper beaufschlagt und zwischen den Kolben im Gehäuse eine ölgefüllte Druckkammer ausgebildet ist, in der sich eine auf die Kolben wirkende Druckfeder befindet, und wobei die Druckkammer über zwischen den Kolben und deren Führungen im Gehäuse bestehende Leckspalte zu einem Ölvorratsraum offen ist, der gegenüber dem Ventil abgedichtet ist.This object is achieved in that a clearance compensation element is arranged between the valve body and the drive member, which has two pistons guided in a housing, the first piston being acted upon by the drive member, the second piston acting on the valve body and between the pistons an oil-filled pressure chamber is formed in the housing, in which there is a pressure spring acting on the pistons, and the pressure chamber is open to an oil storage space, which is sealed off from the valve, via leakage gaps existing between the pistons and their guides in the housing.

Die Druckfeder drückt den ersten Kolben spielfrei gegen das Antriebsglied und den zweiten Kolben gegen den in Öffnungsstellung stehenden Ventilkörper. Zum Schließen des Ventils drückt das Antriebsglied auf den ersten Kolben. Über die Ölfüllung wird dadurch der zweite Kolben verschoben, der den Ventilkörper so beaufschlagt, daß das Ventil schließt. Durch die Ölfüllung ist eine hohe Steifigkeit des Antriebs gewährleistet. Insbesondere ist günstig, daß die Ölfüllung der Druckkammer unabhängig von dem Kraftstoff nach den notwendigen Eigenschaften hinsichtlich der Viskosität und dem Temperaturverhalten ausgewählt werden kann.The compression spring presses the first piston against the drive member without play and the second piston against the valve body in the open position. To close the valve, the drive member presses on the first piston. As a result, the second piston, which acts on the valve body in such a way that the valve closes, is moved over the oil filling. The oil filling ensures high rigidity of the drive. In particular, it is favorable that the oil filling of the pressure chamber can be selected independently of the fuel according to the necessary properties with regard to viscosity and temperature behavior.

Die Kolben weisen eine im Vergleich zum Gehäuse geringe Masse auf. Dies verbessert die dynamischen Eigenschaften des Gesamtsystems.The pistons have a low mass compared to the housing. This improves the dynamic properties of the overall system.

Durch eine unterschiedliche Gestaltung der Durchmesser der beiden Kolben ist es möglich, eine Übersetzung oder eine Untersetzung des Hubs des Antriebsgliedes zu erreichen.Due to a different design of the diameter of the two pistons it is possible to achieve a translation or a reduction in the stroke of the drive member.

In bevorzugter Ausgestaltung der Erfindung ist im Gehäuse zwischen dem Ölvorratsraum und der Druckkammer ein Rückschlagventil angeordnet, durch das bei einer Entspannung öl in den Druckraum eintritt. Dadurch ist gewährleistet, daß trotz Ölverlusten über die Leckspalte der Druckraum ölgefüllt bleibt.In a preferred embodiment of the invention, a check valve is arranged in the housing between the oil reservoir and the pressure chamber oil enters the pressure chamber when the pressure is released. This ensures that the pressure chamber remains oil-filled despite oil losses through the leakage gaps.

Weitere vorteilhafte Ausgestaltungen der Erfindung ergeben sich aus den Unteransprüchen und der folgenden Beschreibung eines Ausführungsbeispiels. Die Figur zeigt ein an einem Ventil angeordnetes Ausgleichselement im Teilschnitt.Further advantageous refinements of the invention result from the subclaims and the following description of an exemplary embodiment. The figure shows a compensating element arranged on a valve in partial section.

In einem Ventilgehäuse(1) ist ein Ventilkörper(2) verschieblich gelagert. Zwischen dem Ventilkörper(2) und dem Ventilgehäuse(1) ist ein Ventilsitz(3) ausgebildet. In der Figur ist der Ventilkörper(2) in seiner Öffnungsstellung gezeigt, in der er mittels einer Druckfeder(4) gegen einen Anschlagring(5) gedrückt ist. Der Ventilsitz(3) bildet dabei einen Flüssigkeitsdurchlaß. Der Hub des Ventilkörpers(2) ist kleiner als 1 mm.A valve body (2) is slidably mounted in a valve housing (1). A valve seat (3) is formed between the valve body (2) and the valve housing (1). The figure shows the valve body (2) in its open position, in which it is pressed against a stop ring (5) by means of a compression spring (4). The valve seat (3) forms a liquid passage. The stroke of the valve body (2) is less than 1 mm.

Der Ventilkörper(2) weist eine zylindrische Führungsfläche(6) auf, deren Durchmesser etwa dem Durchmesser des Ventilsitzes(3) gleich ist. Zwischen der Führungsfläche(6) und dem Ventilsitz(3) ist am Ventilkörper(2) eine Umfangsausnehmung(7) ausgebildet, die zu einem Ringkanal(8) des Ventilgehäuses(1) offen ist. In den Ringkanal(8) mündet eine Bohrung(9). An der dem Ringkanal(8) abgewandten Seite des Ventilsitzes(3) ist ein Auslaß(10) vorgesehen.The valve body (2) has a cylindrical guide surface (6), the diameter of which is approximately the same as the diameter of the valve seat (3). A circumferential recess (7) is formed on the valve body (2) between the guide surface (6) and the valve seat (3) and is open to an annular channel (8) of the valve housing (1). A bore (9) opens into the annular channel (8). An outlet (10) is provided on the side of the valve seat (3) facing away from the annular channel (8).

Die Bohrung(9) ist an eine von einer Einspritzpumpe zur Einspritzdüse eines Zylinders eines Verbrennungsmotors führende Kraftstoff-Einspritzleitung angeschlossen. Der Auslaß(10) führt zur Ansaugseite der Einspritzpumpe zurück. Solange der Ventilkörper(2) in seiner Öffnungsstellung steht, besteht an der Einspritzdüse kein zum Einspritzen hinreichender Druck. Wird der Ventilkörper(2) in seine Schließstellung gebracht, dann baut sich an der Einspritzdüse ein gewünschter, hoher Einspritzdruck, von beispielsweise 1000 bar auf.The bore (9) is connected to a fuel injection line leading from an injection pump to the injection nozzle of a cylinder of an internal combustion engine. The outlet (10) leads back to the suction side of the injection pump. As long as the valve body (2) is in its open position, there is no sufficient pressure at the injection nozzle to inject. Will the When the valve body (2) is brought into its closed position, a desired, high injection pressure of, for example, 1000 bar builds up on the injection nozzle.

Der Ventilkörper(2) weist eine zum Innenraum(11) des Anschlagrings(5) offene Druckausgleichsbohrung(12) auf. In dem Innenraum(11) kann sich Kraftstoff sammeln.The valve body (2) has a pressure compensation bore (12) that is open to the interior (11) of the stop ring (5). Fuel can collect in the interior (11).

An den Anschlagring(5) ist gegenüber dem Ventilgehäuse(1) ein Gehäuse(13) eines Ausgleichselements(14) angesetzt. In dem Gehäuse(13) ist ein erster Kolben(15) geführt. An diesem ist ein Rückschlagventil(l6), bestehend aus einer Haltekappe(17) und einer sich an dieser über eine Schließfeder(18) abstützenden Ventilkugel(19) angeordnet. Der Ventilkugel(19) ist ein Kugelsitz(20) einer Höhlung(21) des ersten Kolbens(15) zugeordnet.A housing (13) of a compensating element (14) is attached to the stop ring (5) opposite the valve housing (1). A first piston (15) is guided in the housing (13). A non-return valve (16), consisting of a retaining cap (17) and a valve ball (19) which is supported thereon by a closing spring (18), is arranged on this. The valve ball (19) has a ball seat (20) associated with a cavity (21) in the first piston (15).

Im Gehäuse(13) ist außerdem ein zweiter Kolben(22) geführt, der aus Vollmaterial besteht und von einer geschliffenen Nadel, wie sie von Nadellagern bekannt ist, gebildet ist.In the housing (13) a second piston (22) is also made, which consists of solid material and is formed by a ground needle, as is known from needle bearings.

Zwischen dem ersten Kolben(15) und dem zweiten Kolben(22) ist eine ölgefüllte Druckkammer(23) ausgebildet. In der Druckkammer(23) ist eine Druckfeder(24) angeordnet, die sich einerseits über den Rand der Haltekappe(17) am ersten Kolben(15) und andererseits über eine Zwischenplatte(25) am zweiten Kolben(22) abstützt. Der Durchmesser des ersten Kolbens(15) ist größer als der Durchmesser des zweiten Kolbens(22).An oil-filled pressure chamber (23) is formed between the first piston (15) and the second piston (22). A pressure spring (24) is arranged in the pressure chamber (23) and is supported on the one hand by the edge of the retaining cap (17) on the first piston (15) and on the other hand by an intermediate plate (25) on the second piston (22). The diameter of the first piston (15) is larger than the diameter of the second piston (22).

Zwischen dem ersten Kolben(15) und dem Gehäuse(13) besteht ein Leckspalt(26). Zwischen dem zweiten Kolben(22) und dem Gehäuse(13) besteht ein Leckspalt (27). Der Leckspalt(26) ist zu einem Ringraum(28) offen, der über einen Durchgang(29) mit der Höhlung(21) verbunden ist. Der Leckspalt(27) ist zu einem Ringraum(30) hin offen, der über wenigstens eine Bohrung(31) mit dem Ringraum(28) in Verbindung steht. Die Höhlung(21), die Ringräume(28,30) und die Bohrung(31) bilden gemeinsam einen ölgefüllten Ölvorratsraum.There is a leakage gap (26) between the first piston (15) and the housing (13). There is a leakage gap (27) between the second piston (22) and the housing (13). The leak gap (26) is open to an annular space (28) which is connected to the cavity (21) via a passage (29). The leakage gap (27) is open to an annular space (30) which is connected to the through at least one bore (31) Annulus (28) is connected. The cavity (21), the annular spaces (28,30) and the bore (31) together form an oil-filled oil storage space.

Um den Öldurchtritt durch die Leckspalte(26,27) möglichst gering zu halten, sind einerseits enge Passungen vorgesehen. Andererseits sind die Kolben(15,22) bezogen auf den zur Verfügung stehenden Bauraum möglichst lang ausgelegt. Die Länge des zweiten Kolbens(22) ist größer als dessen Durchmesser.In order to keep the oil passage through the leakage gaps (26, 27) as low as possible, close fits are provided on the one hand. On the other hand, the pistons (15, 22) are designed to be as long as possible in relation to the available installation space. The length of the second piston (22) is greater than its diameter.

Der Ringraum(30) ist gegenüber dem Innenraum(11) mittels einer Membrananordnung(32) abgedichtet. Die Membrananordnung(32) weist eine Platte(33) auf, die zwischen dem zweiten Kolben(22) und dem Ventilkörper(2) liegt. Die Platte(33) ist an ihrem Umfang mit einer im Querschnitt teilkreisförmigen Rille(34) versehen. An die Rille(34) und deren Ränder(35) ist ein elastischer Ring(36) aus Gummi vulkanisiert. Es ist dabei eine vergleichsweise große Verbindungsfläche zwischen der Platte(33) und dem Ring(36) erreicht. Der elastische Ring(36) ist an seinem Außenumfang an eine Hülse(37) vulkanisiert. Diese sitzt in Preßpassung in einer Bohrung(38) des Gehäuses(13).The annular space (30) is sealed off from the interior (11) by means of a membrane arrangement (32). The membrane arrangement (32) has a plate (33) which lies between the second piston (22) and the valve body (2). The plate (33) is provided on its circumference with a groove (34) which is partially circular in cross section. An elastic ring (36) made of rubber is vulcanized to the groove (34) and its edges (35). A comparatively large connecting area between the plate (33) and the ring (36) is achieved. The elastic ring (36) is vulcanized on its outer circumference to a sleeve (37). This sits in a press fit in a bore (38) of the housing (13).

Der Ringraum(28) ist mit einer ähnlichen Membrananordnung(39) gegenüber der Umgebung abgedichtet. Die Membrananordnung(39) weist eine Platte(40) mit einer im Querschnitt halbkreisförmigen Rille(41) auf. An diese und deren Ränder(42) ist ein elastischer Ring(43) aus Gummi vulkanisiert. Der Außenumfang des Rings(43) ist an eine Hülse(44) vulkanisiert, die in Preßpassung in eine Bohrung(45) des Gehäuses(13) eingesetzt ist. Die Platte(40) ist mit einer Einfüllöffnung(46) für Öl versehen, die mit einem Stopfen(47) verschlossen ist. Die Platte(40) liegt an dem ersten Kolben(15) an. An ihrer diesem abgewandten Seite liegt das nicht näher dargestellte Antriebsglied an.The annular space (28) is sealed off from the environment with a similar membrane arrangement (39). The membrane arrangement (39) has a plate (40) with a groove (41) which is semicircular in cross section. An elastic ring (43) made of rubber is vulcanized to these and their edges (42). The outer circumference of the ring (43) is vulcanized to a sleeve (44) which is press-fitted into a bore (45) in the housing (13). The plate (40) is provided with a filling opening (46) for oil, which is closed with a stopper (47). The plate (40) abuts the first piston (15). On its side facing away from this lies the drive member, not shown.

Die elastischen Ringe(36,43) können auch von Kunststoffteilen oder Blechteilen gebildet sein.The elastic rings (36, 43) can also be formed from plastic parts or sheet metal parts.

Die Funktionsweise der beschriebenen Einrichtung ist ausgehend von der in der Figur dargestellten Stellung etwa folgende:
Durch die Bohrung(9), den Ringkanal(8), die Umfangsausnehmung(7), den Ventilsitz(3) und den Auslaß(10) wird von der Einspritzpumpe Kraftstoff gepumpt. Die zugehörige Einspritzdüse ist dabei geschlossen. Die Druckfeder(4) hält den Ventilsitz(3) offen. Die Druckkammer(23) und der Ölvorratsraum sind ölgefüllt. Unter der Wirkung der Druckfeder(24), die schwächer ist als die Druckfeder(4), ist der erste Kolben(15) über die Platte(40) spielfrei an das Antriebsglied und der zweite Kolben(22) spielfrei über die Platte(33) an den Ventilkörper(2) gedrückt.Starting from the position shown in the figure, the functioning of the described device is approximately as follows:
The injection pump pumps fuel through the bore (9), the annular channel (8), the peripheral recess (7), the valve seat (3) and the outlet (10). The associated injector is closed. The compression spring (4) keeps the valve seat (3) open. The pressure chamber (23) and the oil reservoir are filled with oil. Under the action of the compression spring (24), which is weaker than the compression spring (4), the first piston (15) is free of play via the plate (40) to the drive member and the second piston (22) is free of play via the plate (33) pressed against the valve body (2).

Wird nun das Antriebsglied betätigt, dann verschiebt es über die Platte(40) den ersten Kolben(15). Dieser verdrängt das Öl der Druckkammer(23). Dadurch wird der zweite Kolben(22) der Übersetzung entsprechend versetzt. Er drückt entgegen der Kraft der Druckfeder(4) so auf die Platte(33), daß der Ventilsitz(3) schließt. Dadurch baut sich im Ringkanal(8) und damit auch an der Einspritzdüse der gewünschte Druck auf.If the drive member is now actuated, it moves the first piston (15) over the plate (40). This displaces the oil in the pressure chamber (23). As a result, the second piston (22) is displaced in accordance with the translation. He presses against the force of the compression spring (4) on the plate (33) so that the valve seat (3) closes. As a result, the desired pressure builds up in the ring channel (8) and thus also at the injection nozzle.

Die über den ersten Kolben(15), die Ölfüllung der Druckkammer(23) und den zweiten Kolben(22) zu übertragende Zuhaltekraft für den Ventilsitz(3) ist vergleichsweise gering, da der Durchmesser des Ventilsitzes(3) einerseits des Ringkanals(8) und der Durchmesser der Führungsfläche(6) andererseits des Ringkanals(8) im wesentlichen gleich groß sind.The locking force to be transmitted for the valve seat (3) via the first piston (15), the oil filling of the pressure chamber (23) and the second piston (22) is comparatively low, since the diameter of the valve seat (3) on the one hand of the ring channel (8) and the diameter of the guide surface (6) on the other hand of the ring channel (8) are substantially the same size.

Solange der Ventilkörper(2) in Schließstellung gehalten ist, tritt über die Leckspalte(26,27) Öl aus der Druckkammer(23) in die Ringräume(28,30). Die Schließstellung des Ventilsitzes(3) bleibt jedoch aufrechterhalten.As long as the valve body (2) is kept in the closed position is, oil leaks from the pressure chamber (23) into the annular spaces (28, 30) via the leakage gaps (26, 27). However, the closed position of the valve seat (3) is maintained.

Schaltet das Antriebsglied ab, dann kann die Druckfeder(4) über die Platte(33) den zweiten Kolben(22) und dadurch den ersten Kolben(15) mit der Platte(40) zurückdrücken. Die Platte(40) bleibt dabei in Anlage am Antriebsglied.If the drive element switches off, the compression spring (4) can push back the second piston (22) and thereby the first piston (15) with the plate (40) via the plate (33). The plate (40) remains in contact with the drive member.

Sobald der Ventilkörper(2) am Anschlagring(5) anschlägt, kann sich die Druckfeder(24) weiter entspannen, was mit einer Volumenvergrößerung der Druckkammer(23) verbunden ist. Dadurch entsteht in dieser ein Unterdruck gegenüber dem Ölvorratsraum. Die Ventilkugel (19) hebt dabei vom Kugelsitz(20) ab, so daß in die Druckkammer(23) Öl nachgefüllt wird.As soon as the valve body (2) strikes the stop ring (5), the compression spring (24) can relax further, which is associated with an increase in volume of the pressure chamber (23). This creates a negative pressure in relation to the oil reservoir. The valve ball (19) lifts off the ball seat (20) so that oil is refilled into the pressure chamber (23).

Claims (7)

  1. Control device comprising a valve (1, 2) which is arranged via its inlet bore (9) at a fuel injection pipe of an internal combustion engine and with its outlet duct (10) at the suction end of the injection pump and whose valve body (2) is pushed against a valve seat (3) by a driving element, characterized in that a clearance compensation element (14) is arranged between the valve body (2) and the driving element, which clearance compensation element (14) comprises two pistons (15, 22) guided in a housing (13), the first piston (15) being acted upon by the driving element, the second piston (22) acting on the valve body (2) and an oil-filled pressure chamber (23) being formed between the pistons (15, 22) in the housing (13), in which pressure chamber (23) a compression spring (24) acting on the pistons (15, 22) is located, the pressure chamber (23) communicating via leak gaps (26, 27) existing in the housing (13) between the pistons (15, 22) and the piston guides with an oil reservoir (28, 30, 31) which is sealed from the valve (1, 2).
  2. Control device according to claim 1, characterized in that a non-return valve (16) is arranged between the oil reservoir (28, 30, 31) and the pressure chamber (23) in the housing (13), through which non-return valve (16), on relaxation of the compression spring (24), oil enters the pressure chamber (23).
  3. Control device according to claim 1 or 2, characterized in that the compression spring (24) is designed to be weaker than a spring (4) which displaces the valve body (2) into its opening position.
  4. Control device according to one of the preceding claims, characterized in that the valve body (2) stops in its opening position in such a way, that a residual travel remains for the relaxation of the compression spring (24).
  5. Control device according to one of the claims 2 to 4, characterized in that the non-return valve (16) is arranged on the first piston (15).
  6. Control device according to one of the preceding claims, characterized in that the length of the second piston (22) is larger than its diameter.
  7. Control device according to one of the preceding claims, characterized in that the oil reservoir (28,30,31) is closed at both ends by a membrane arrangement (32, 39) comprising a plate (33, 40) bearing against the first and second piston (15, 22) respectively, the plate (33, 40) being surrounded by an elastic ring (36, 43) fixed to a sleeve (37, 44) located in the housing (13) in an interference fit.
EP19880101417 1987-02-14 1988-02-02 Valve control device Expired - Lifetime EP0279267B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3704743 1987-02-14
DE19873704743 DE3704743A1 (en) 1987-02-14 1987-02-14 CONTROL VALVE FOR A VALVE

Publications (2)

Publication Number Publication Date
EP0279267A1 EP0279267A1 (en) 1988-08-24
EP0279267B1 true EP0279267B1 (en) 1991-07-03

Family

ID=6321029

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19880101417 Expired - Lifetime EP0279267B1 (en) 1987-02-14 1988-02-02 Valve control device

Country Status (5)

Country Link
US (1) US4840160A (en)
EP (1) EP0279267B1 (en)
JP (1) JPS63201367A (en)
DE (2) DE3704743A1 (en)
ES (1) ES2022930B3 (en)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5421521A (en) * 1993-12-23 1995-06-06 Caterpillar Inc. Fuel injection nozzle having a force-balanced check
GB2289313B (en) * 1994-05-13 1998-09-30 Caterpillar Inc Fluid injector system
US5697342A (en) * 1994-07-29 1997-12-16 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US6082332A (en) * 1994-07-29 2000-07-04 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US5463996A (en) * 1994-07-29 1995-11-07 Caterpillar Inc. Hydraulically-actuated fluid injector having pre-injection pressurizable fluid storage chamber and direct-operated check
US6575137B2 (en) 1994-07-29 2003-06-10 Caterpillar Inc Piston and barrel assembly with stepped top and hydraulically-actuated fuel injector utilizing same
US5687693A (en) * 1994-07-29 1997-11-18 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US5826562A (en) * 1994-07-29 1998-10-27 Caterpillar Inc. Piston and barrell assembly with stepped top and hydraulically-actuated fuel injector utilizing same
WO2000034646A1 (en) 1998-12-11 2000-06-15 Caterpillar Inc. Piston and barrel assembly with stepped top and hydraulically-actuated fuel injector utilizing same
DE10046323B4 (en) * 2000-09-19 2004-02-12 Siemens Ag Hydraulic backlash compensation system
US8132558B2 (en) * 2009-12-01 2012-03-13 Stanadyne Corporation Common rail fuel pump with combined discharge and overpressure relief valves
CN114715287B (en) * 2022-03-01 2023-03-24 浙江零跑科技股份有限公司 C-pillar structure of parallel door

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE256641C (en) *
FR426106A (en) * 1910-04-23 1911-06-28 Amedee Bollee Fils Automatic adjustment of the play in the valve train
FR15118E (en) * 1910-04-23 1912-04-26 Amedee Bollee Fils Automatic adjustment of the play in the valve train
US2524799A (en) * 1949-01-07 1950-10-10 American Cyanamid Co Hydroxybenzenesulfonamidoimidazoles and preparation of the same
DE1289359B (en) * 1966-08-30 1969-02-13 Kloeckner Humboldt Deutz Ag Fuel injection system
US3495577A (en) * 1968-02-07 1970-02-17 Clifford H Collins Self-contained hydraulic tappet
DE2348865A1 (en) * 1973-09-28 1975-04-10 Maschf Augsburg Nuernberg Ag Fuel injector system for compression ignition engines - has pressure relief valve fitted inside pump delivery valve to relieve pressure oscillations
US3965826A (en) * 1975-05-05 1976-06-29 H C Products Co. Shelving structure
GB2013275B (en) * 1978-01-31 1982-06-30 Lucas Industries Ltd Liquid fuel pumping apparatus
DE3048347A1 (en) * 1980-12-20 1982-07-22 Volkswagenwerk Ag, 3180 Wolfsburg FUEL INJECTION DEVICE
IT1150318B (en) * 1981-03-21 1986-12-10 Bosch Gmbh Robert FUEL INJECTION PUMP FOR ENDOTHERMAL ENGINES
DE3138211A1 (en) * 1981-09-25 1983-04-07 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
US4478189A (en) * 1982-12-08 1984-10-23 Lucas Industries Fuel injection system
DE3341575C2 (en) * 1983-11-17 1996-06-05 Bosch Gmbh Robert Pressure valve for fuel injection pumps
DE3344825A1 (en) * 1983-12-12 1985-06-13 Robert Bosch Gmbh, 7000 Stuttgart PRESSURE VALVE FOR FUEL INJECTION PUMPS
US4497298A (en) * 1984-03-08 1985-02-05 General Motors Corporation Diesel fuel injection pump with solenoid controlled low-bounce valve
DE3417210A1 (en) * 1984-05-10 1985-11-14 Robert Bosch Gmbh, 7000 Stuttgart PRESSURE VALVE
US4762386A (en) * 1986-09-02 1988-08-09 Amp Incorporated Optical fiber assembly including means utilizing a column load to compensate for thermal effects

Also Published As

Publication number Publication date
DE3863439D1 (en) 1991-08-08
DE3704743A1 (en) 1988-08-25
EP0279267A1 (en) 1988-08-24
JPS63201367A (en) 1988-08-19
ES2022930B3 (en) 1991-12-16
US4840160A (en) 1989-06-20

Similar Documents

Publication Publication Date Title
EP0733798B1 (en) Fuel injection device working according to the solid energy accumulator principle, for internal combustion engines
EP0279267B1 (en) Valve control device
DE19817320C1 (en) Injector for fuel injection systems
DE102007001363A1 (en) Injector for injecting fuel into combustion chambers of internal combustion engines
DE102015100662A1 (en) Hydraulic valve for switching a control piston of a connecting rod
DE69814990T2 (en) Injector
DE10020867B4 (en) Common rail injector
WO2018083256A1 (en) Adjustable-length connecting rod having a piston/cylinder unit having cylinder sleeve
DE112009001971T5 (en) Check valve with separate spherical spring guide
DE3928612A1 (en) FUEL DISTRIBUTOR INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
EP0941401B1 (en) Liquid control valve
DE60017029T2 (en) Fuel pump
WO2003052261A1 (en) Device for the translation of a displacement of an actuator, in particular for an injection valve
DE102008000301B4 (en) injector
DE10112147A1 (en) Valve for controlling liquids
EP2519732B1 (en) Electromagnetically actuated metering control valve, particularly for controlling the flow of a high pressure fuel pump
DE102010040612A1 (en) Hydraulic temperature compensator and hydraulic lift transmitter
DE102016120950A1 (en) Connecting rod with encapsulated assembly for length adjustment
DE102008000317B4 (en) fuel injector
DE102010027608A1 (en) Control assembly for internal combustion engine, comprises hydraulic valve clearance lifter element, where compensation element has circular cylindrical lifter housing that is axially extended towards camshaft over its base
DE2517370A1 (en) Hydraulic clearance compensating device for IC engine valves - has hydraulic medium filled pre-chamber sealed with elastic membrane
DE102016120943A1 (en) Connecting rod with adjusting mechanism between connecting rod and piston rod
DE102015121918A1 (en) Changeover valve, connecting rod and internal combustion engine
EP1798415B1 (en) High pressure pump
DE102016120942A1 (en) Connecting rod with stepped piston

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19880202

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE ES FR GB IT

17Q First examination report despatched

Effective date: 19890803

ITF It: translation for a ep patent filed

Owner name: DE DOMINICIS & MAYER S.R.L.

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR GB IT

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
REF Corresponds to:

Ref document number: 3863439

Country of ref document: DE

Date of ref document: 19910808

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19930125

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19930204

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 19930212

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19940202

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19940203

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19940202

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19941031

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19980205

Year of fee payment: 11

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 19990301

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19991201

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050202