EP0852666B1 - Fuel injection pump with an injection adjusting piston which adjusts the injection beginning - Google Patents

Fuel injection pump with an injection adjusting piston which adjusts the injection beginning Download PDF

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Publication number
EP0852666B1
EP0852666B1 EP97922883A EP97922883A EP0852666B1 EP 0852666 B1 EP0852666 B1 EP 0852666B1 EP 97922883 A EP97922883 A EP 97922883A EP 97922883 A EP97922883 A EP 97922883A EP 0852666 B1 EP0852666 B1 EP 0852666B1
Authority
EP
European Patent Office
Prior art keywords
injection
adjusting piston
recess
fuel injection
piston
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
EP97922883A
Other languages
German (de)
French (fr)
Other versions
EP0852666A1 (en
Inventor
Wolfgang Geiger
Thomas Kulder
Andreas Sterr
Walter Fuchs
Bernd Berghaenel
Dieter Reitz
Wolfgang Fehlmann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Adam Opel GmbH
Original Assignee
Robert Bosch GmbH
Adam Opel GmbH
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Publication date
Application filed by Robert Bosch GmbH, Adam Opel GmbH filed Critical Robert Bosch GmbH
Publication of EP0852666A1 publication Critical patent/EP0852666A1/en
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Publication of EP0852666B1 publication Critical patent/EP0852666B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/16—Adjustment of injection timing
    • F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/16—Adjustment of injection timing
    • F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
    • F02D1/183—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/14—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons
    • F02M41/1405—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis
    • F02M41/1411—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis characterised by means for varying fuel delivery or injection timing
    • F02M41/1416—Devices specially adapted for angular adjustment of annular cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/16—Adjustment of injection timing
    • F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
    • F02D1/183—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic
    • F02D2001/186—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic using a pressure-actuated piston for adjustment of a stationary cam or roller support

Definitions

  • the invention is based on a fuel injection pump the genus of claim 1 from (see DE 115 5290 B).
  • a fuel injection pump the genus of claim 1 from (see DE 115 5290 B).
  • an injection pump is known in which Pump interior the control pressure for spray start adjustment is pending and this pressure over the middle area Injection-adjustable piston and the control spool is fed.
  • the spool is there in an area of the Injection-adjusting piston on the side of an as Restoring force, one end of the Sprayer piston leaving spring in a bore of the injection adjustment piston.
  • the one from the spool in this Bore limited pressure chamber is within the Injection-adjusting piston and the control spring are supported parallel to the load on the spray adjustment piston Return spring fixed to the housing.
  • This version of the Injection-adjusting piston is one of those attacking it Forces loaded symmetrically, so that no essential Act on it.
  • this construction requires a different one Supply of the control pressure medium in the middle area of the injection piston must be provided and the additionally builds up a pressure field on the spray adjustment piston, which, in turn, loads the spray-adjusting piston radially and partly the radial forces resulting from the overturning moment reinforced between the injection adjustment piston and the cylinder.
  • the coupling part in the recess in the injection piston a pressure room in which a second pressure field is generated, which counteracts the first pressure field, the from the recess loaded by the pressure medium source is produced.
  • the pressure field is on the the injection piston opposite side through the in the housing of the Fuel injection pump mounted coupling part of the Intercepted cam drive.
  • Another advantageous embodiment of the invention is that according to claim 6 between the Shell surface of the injection piston and the wall of the An additional recess is provided in the cylinder whose area the second pressure field is formed, the compensating for that from the first pressure field and from the The tilting moment caused by the cam drive acts.
  • This execution requires an additional constructive effort the above configuration, but is related to the necessary in the first-mentioned configuration Sealing the pressure chamber is less problematic.
  • the recess and the additional are advantageous Recess made as a longitudinal slot and are in a common ring area of the lateral surface of the Spritzverstell flask.
  • connection between the recess in the essential opposite points between the Shell surface of the injection piston and the wall of the Cylinder can be realized in that the to these Make leading connection channels between the Cylinder sleeve and the housing are incorporated as gutters.
  • To improve the sealing of the injection adjustable piston working space enclosed in the cylinder has this one metallic, elastic to the inner Apply the outer surface of the cylinder or the cylinder sleeve Sealing ring on. This is also in the areas of Injection-adjusting pistons that do not have such high radial forces is exposed, the sealing of the work area guaranteed.
  • FIG. 1 shows a first Embodiment of the invention with one of Coupling part and injection adjuster piston included Pressure space to provide a compensating second Pressure field
  • Figure 2 shows a longitudinal section through the Embodiment according to Figure 1 along the line II-II in Figure 1 with a second embodiment of the invention using a compensating compression spring
  • Figure 3 a third embodiment of the invention, shown in Shape of a longitudinal section through an injection piston the fuel injection pump
  • Figure 4 shows a section through the embodiment of Figure 3 along the line IV-IV of Figure 3
  • Figure 5 shows a fourth embodiment of the Invention based on a longitudinal section through a Injection-adjustable pistons with a first variant of the Guides of the connecting channels
  • Figure 6 a modification of the embodiment of Figure 5 with a second Variant of the connection channels, shown on a cylinder, in which the cylinder sleeve according to Figure 5 and the Spray adjuster pistons are not yet installed.
  • Fuel injection pumps of the distributor type can either as pumps with one as both distributor and Pump piston serving, axially driven pump piston can be provided, or radial pistons can be provided are arranged radially in a manifold Promote the delivery channel. In both cases, the Pump piston through one of the drive shaft of the Fuel injection pump actuated moving cam drive. Part of such a so-called radial piston pump is in the Section shown in Figure 1. In such pumps, for. B. four pump pistons, not shown here, provided in at the same angular distance from each other together radially to Radial bores in the axis of the distributor Distributors are mounted tightly displaceable.
  • cam track 2 Part of cam track 2 is shown, which is arranged on the inside of a cam ring 3 and which the pump pistons follow.
  • the cam ring 3 represents the essentially stationary part of the cam drive Pump piston represents. While the moving the pump piston Facility that z. B. the ring leading the roller tappet or distributor that can be with the drive shaft is coupled, the moving part of the cam drive represents.
  • the outer circumference of the cam ring is in a cylindrical recess 5 in the housing 6 of the Fuel injection pump stored and can be in one level perpendicular to the drive axis of the fuel injection pump be twisted.
  • the cam ring 3 has a torsion Coupling part in the form of an integral part of this radially outwardly projecting pin 7, which in a recess 9 of an injection adjusting piston 10 is immersed.
  • the spray adjustment piston is sealed in a cylinder 11 displaceable and closes with its one end face 12 the closed end of the cylinder 11 a working space 14 one and with its other end face in there as well closed cylinder 11 a spring chamber 15.
  • a return spring 16 is arranged, the one hand on a closing part 17 and on the other hand, on the end face 19 of the injection adjustment piston 10 supports and strives so clamped, the Injection-adjusting piston with one end face 12 in Facing the cylinder 11 opposite closing wall 20 or a stop arranged there bring to.
  • a cylinder bore in the injection adjustment piston 10 22 provided in the form of an axial blind bore, which by the end face 19 goes out.
  • One used there Control slide 24 closes with its one end face 25 with the closed end of the blind hole pressure-relieved end space in which a compression spring 27 is clamped, the spool 24 on this Face 25 loaded and him with his other end in Holds on a plunger 28 which in the spring chamber 15th dips.
  • This plunger has a spring plate 29 there on which a control spring 30 is supported, which on the other hand is supported on the closure part 17.
  • the pestle is in a bore 31 of the closure member 17 out and protrudes in a cylinder 32, which is inside the closure part 17th is arranged.
  • control spring 30 The coaxial and parallel to the return spring 16 in the spring chamber 15 arranged control spring 30 is flushed with fuel, of the leakage or discharge amount from the spring chamber 15 a relief room is supplied.
  • the spring chamber 15 is also that of the piston 33 in the cylinder 32 enclosed space 38 connected via a Axial bore 36 in the plunger 28, which has a radial bore 37 has its exit on the tappet within the spring chamber 15.
  • the control slide 24 has three close to each other lying ring bundles, of which a first ring bundle 39, the spring chamber side has a control edge on the spring chamber side 40, about which not one here in the drawing shown, from the axial blind bore 22 to the working space 14 leading relief channel 41 at a particular Relative position of control spool 24 and spray-adjusting piston 10 is opened towards each other towards the spring chamber 15.
  • This relief channel 41 is shown in FIG. 2.
  • the first ring collar 39 follows the side of the working space 14 a second collar 43, which is the control of the spool serves and at the same time the mitigation of a pressure relief surge.
  • This ring collar 43 is then followed by a third ring collar 45, a control edge 46 to the side of the working space 14 has one of the axial blind bore outgoing filling channel 48, which via a check valve 49 opens into the work space 14, is controlled.
  • a control edge Provides this Control edge the connection between the outlet 50 of the Filling channel 48 with one to the side of the working space 14 to the control edge ring groove 51 forth, so thereby fuel from this annular groove under control pressure at the same time there is actuating pressure via the filling channel in the work space 14 slides.
  • the ring groove is constantly over an inflow channel 53 with a recess 54 in the The outer surface of the spray adjustment piston is connected.
  • a pressure medium inlet 55 which is preferably from the Control pressure source that also produces the work space 34 provided.
  • the assignment of this Lägnsnut to the confluence of the Pressure medium inlet 55 in the cylinder is through the Coupling the Spritzverstell-piston 10 with the pin 7 of Guaranteed cam ring.
  • the position of this is in FIG Longitudinal groove 54 can be removed, the symbolic in Figure 1 only is shown in dashed lines.
  • the recess 9 in the outer surface of the injection piston is circular in cross section, so that the Pin 7 a pressure chamber 57 in this recess includes.
  • This pressure chamber has a short bore 58 in constant connection with the ring groove 51 and is the Tax pressure exposed.
  • the housing 6 In the area of the entry of the pin 7 into the recess the housing 6 has an interior 4 of the Fuel injection pump with the cylinder 11 connecting Recess 60 such that the pin 7 the Adjustment movements of the spray adjustment piston 10 unimpeded can follow. In this area, the outer surface of the Spritzverstell-piston 10 a low interior pressure Fuel pump exposed to the order of magnitude Relief pressure is, so the injection piston not significantly loaded radially.
  • the injection piston at the high on it acting forces are carried out with as little wear as possible can take into account the fact that the housing 6 the injection pump, for example made of die-cast aluminum there is a cylinder sleeve 61 provided as a cylinder, which is made of high quality steel and in a corresponding cylindrical bore of the housing inserted or pressed is.
  • the injection adjustment piston itself also consists of high quality steel, which also has a corresponding Surface coating to increase wear resistance can have.
  • an annular groove 63 incorporated into the metallic piston ring 64 is set, which is a high quality Sealing guaranteed.
  • the spray adjustment piston 10 and the piston 33 together with the plunger 28 and springs 16 and 30 require a certain amount of space.
  • the spray adjustment piston is on the Side of the spring chamber 15 is kept shorter for this reason, thus certain predetermined dimensions of the spray adjuster can be maintained.
  • the spool extends therefore, in order to save space, in particular via the Area where the cam ring 3 over the pin 7 with the Injection adjustment piston 10 is coupled.
  • the pressure field, that emerges from the longitudinal groove 54 as the first pressure field is shown in 2 schematically shown as the first pressure field 66. It increases along with the tracking forces that come from the Tipping moment result, the surface pressure on the side of the cam ring between the injection piston 10 and Cylinder 11. Increased forces in connection with Material properties and roughness of the material pairings can lead to component failure.
  • the pin 7 encloses the pressure chamber 57 relatively tightly, the peg acts in connection with its end face with the bearing of the cam ring 3 as a support surface.
  • the pin is preferably at the connection point for spherical injection-adjustable piston 10. Too keeping the wear down here are the parts that touch each other here, hardened. In particular, the Injection-adjusting piston 10 for reasons of wear casehardened.
  • the second pressure field which was realized in the pressure chamber 57, is realized in the form of an additional longitudinal groove 67 in the lateral surface of the injection-adjusting piston according to the embodiment according to FIG. 1.
  • the piston and its drive are constructed essentially the same as in the exemplary embodiment according to FIG. 1. Reference can therefore be made to the description of this figure in this regard.
  • the section according to FIG. 3 shows a view that results from section III-III of FIG. 4. It can be seen from FIG. 4 that the additional longitudinal groove 67 lies essentially diametrically opposite the longitudinal groove 54. The connection between the annular groove 51 and this additional longitudinal groove 67 takes place via a connecting line 68.
  • the second pressure field building up on the additional longitudinal groove 67 is equivalent to the pressure field building up on the longitudinal groove 54.
  • the forces arising from these pressure fields thus cancel each other out, so that the radial load on the injection-adjusting piston 10 is substantially reduced.
  • the pressure fields can be clearly dimensioned in order to precisely set the desired pressure compensation.
  • an additional groove 71 72 is provided at a short distance and parallel to the longitudinal grooves 67 and 54 on the side facing away from the recess 9, which are longer than these grooves 67 and 54 and projecting on both sides with one end projecting into the spring chamber 15 ,
  • the pressure field is relieved to the spring space at the location of the additional grooves and thus limited in the circumferential direction.
  • FIG. 5 also shows a third exemplary embodiment for relieving the injection adjustment piston 10 of harmful radial forces.
  • This embodiment is also based on the provision of a second pressure field, which is opposite to the first pressure field, but in this case it is divided into two second pressure fields in order to record as much as possible all the moments that occur on the injection adjustment piston 10.
  • the spray adjustment piston with control slide is constructed in the same way as in the exemplary embodiment according to FIGS. 1 and 3, so that a supplementary description in this regard is not necessary.
  • FIG. 1 the spray adjustment piston with control slide is constructed in the same way as in the exemplary embodiment according to FIGS. 1 and 3, so that a supplementary description in this regard is not necessary.
  • a first connecting channel 69 and a second connecting channel 70 are now provided between the cylinder sleeve 61 and the adjacent housing 6 of the fuel injection pump, which, starting from the pressure medium inlet 55, initially run parallel to a surface line of the cylinder sleeve 61 and then in each case a half-ring groove 72 or 73 pass over, which lead to a location on the circumference of the cylinder sleeve 61 which lies diametrically to the entry of the pressure medium inlet 55 into the cylinder 11.
  • the cylinder sleeve has a first opening 75 and a second opening 74, via which the connecting channels 69 and 70 have a connection to the interior of the cylinder 11 in the region between the cylinder 11 and the outer surface of the injection-adjusting piston.
  • second pressure fields build up, which are symbolized as F da in the drawing.
  • These forces are symmetrical to the center line of the pin 7 so that they ensure a uniform force balance on the injection-adjusting piston 10. They counteract the resulting contact forces FA and FB, which result from the loading of the first pressure field in the area of the pressure medium inlet 55. They also counteract at least one force component of the tilting forces exerted by the tilting moment on the actuating piston.
  • FIG. 6 shows an alternative to the ducting of the Connection channels, which here are the first connection channel 69 ' and the second connecting channel 70 'run helically, starting from the pressure medium inlet 55. It is advantageous thereby the elaboration of the connecting channels as grooves that then through the pressed-in cylinder sleeve be closed, except for the inlet and the passages 75 and 74.

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

Description

Stand der TechnikState of the art

Die Erfindung geht von einer Kraftstoffeinspritzpumpe gemäß der Gattung des Patentanspruchs 1 aus (siehe DE 115 5290 B). Durch die DE-A-35 32 719 ist eine Einspritzpumpe bekannt, bei der im Pumpeninnenraum der Steuerdruck zur Spritzbeginnverstellung ansteht und dieser Druck über den mittleren Bereich dem Spritzverstell-Kolben und dem Steuerschieber zugeführt wird. Dabei ist die Verbindung zwischen Spritzverstell-Kolben und dem Nockenantrieb so gestaltet, daß mittig im Bereich der Achse des Spritzverstell-Kolbens ein Gleitstein gelagert ist, in den das Kupplungsteil senkrecht zur Drehbewegung des Gleitsteins eingreifen kann. Der Steuerschieber liegt dabei in einem sich an den Gleitstein anschließenden Bereich des Spritzverstell-Kolbens auf der Seite einer als Rückstellkraft dienenden, eine Stirnseite des Spritzverstellerkolbens belassenden Feder in einer Bohrung des Spritzverstell-Kolbens. Der vom Steuerschieber in dieser Bohrung begrenzte Druckraum liegt innerhalb des Spritzverstell-Kolbens und die Steuerfeder stützt sich parallel zur den Spritzverstell-Kolben belastenden Rückstellfeder gehäusefest ab. Diese Ausführung des Spritzverstell-Kolbens ist von den an ihm angreifenden Kräften symmetrisch belastet, so daß keine wesentlichen Kippmomente auf ihn einwirken.The invention is based on a fuel injection pump the genus of claim 1 from (see DE 115 5290 B). By DE-A-35 32 719 an injection pump is known in which Pump interior the control pressure for spray start adjustment is pending and this pressure over the middle area Injection-adjustable piston and the control spool is fed. Here is the connection between the injection piston and the cam drive designed so that in the center of the A sliding block is mounted on the axis of the spray adjustment piston is in which the coupling part perpendicular to the rotational movement of the Lubricant can intervene. The spool is there in an area of the Injection-adjusting piston on the side of an as Restoring force, one end of the Sprayer piston leaving spring in a bore of the injection adjustment piston. The one from the spool in this Bore limited pressure chamber is within the Injection-adjusting piston and the control spring are supported parallel to the load on the spray adjustment piston Return spring fixed to the housing. This version of the Injection-adjusting piston is one of those attacking it Forces loaded symmetrically, so that no essential Act on it.

Bei höheren Anforderungen an den Spritzversteller ist es erforderlich, den den Steuerschieber beaufschlagenden Druckraum außerhalb des Spritzverstell-Kolbens unterzubringen, was jedoch mit einem höheren Platzbedarf in Achsrichtung des Spritzverstell-Kolbens verbunden ist. Um dieses zu kompensieren, muß der Spritzverstell-Kolben kürzer werden und der Steuerschieber muß in einem Bereich des Spritzverstell-Kolbens untergebracht werden, der zugleich der Kupplung des Spritzverstell-Kolbens mit dem Nockenantrieb dient. Die aufgrund dieser Konstruktion nicht mehr koaxial sondern exzentrisch am Spritzverstell-Kolben angreifenden Rückwirkungskräfte vom Nockenantrieb her erzeugen am Spritzverstell-Kolben Kippmomente, die die Führung des Spritzverstell-Kolbens in seinem Zylinder belasten. Zusätzlich bedingt diese Konstruktion eine andere Zuführung des Steuerdruckmittels, die im mittleren Bereich des Spritzverstell-Kolbens vorgesehen werden muß und die zusätzlich ein Druckfeld am Spritzverstell-Kolben aufbaut, das den Spritzverstell-Kolben wiederum radial belastet und zum Teil die aus dem Kippmoment resultierenden Radialkräfte zwischen Spritzverstell-Kolben und Zylinder verstärkt.With higher demands on the spray adjuster it is required to act on the control spool Pressure space outside of the injection adjustment piston to accommodate what, however, with a higher space requirement in Axial direction of the spray adjustment piston is connected. Around To compensate for this, the injection adjustment piston must be shorter and the control spool must be in an area of the Injection-adjusting pistons can be accommodated at the same time the coupling of the injection adjustment piston with the Cam drive is used. Not because of this construction more coaxial but eccentric on the injection adjustable piston attacking reaction forces from the cam drive generate tilting moments on the injection-adjustable piston which Guidance of the injection adjustment piston in its cylinder strain. In addition, this construction requires a different one Supply of the control pressure medium in the middle area of the injection piston must be provided and the additionally builds up a pressure field on the spray adjustment piston, which, in turn, loads the spray-adjusting piston radially and partly the radial forces resulting from the overturning moment reinforced between the injection adjustment piston and the cylinder.

Vorteile der ErfindungAdvantages of the invention

Durch die erfindungsgemäße Kraftstoffeinspritzpumpe mit den Merkmalen des Kennzeichens wird bei einem Spritzverstell-Kolben, der durch Rückwirkungskräfte vom Nockenantrieb einseitig belastet ist und der zusätzlich eine Druckmittelzufuhr aufweist, die die aus der einseitigen Belastung resultierenden Kräfte verstärkt, nun eine Möglichkeit bereitgestellt, um diese einseitige Belastung des Spritzverstell-Kolbens und seiner Führung zu kompensieren, derart, daß die zwischen Spritzverstell-Kolben und Zylinder senkrecht, einseitig wirkenden Kräfte reduziert werden.By the fuel injection pump according to the invention with the Characteristics of the license plate is in an injection adjustable piston, by reaction forces from the cam drive is burdened on one side and the additional one Has pressure medium supply, which from the one-sided Resulting forces increased, now a Possibility provided to overcome this one-sided burden of the injection adjustment piston and its guide compensate in such a way that between the injection adjustment pistons and cylinder vertical, one-sided forces reduced become.

In vorteilhafter Ausgestaltung schließt gemäß Patentanspruch 4 das Kupplungsteil in der Vertiefung im Spritzverstell-Kolben einen Druckraum ein, in dem ein zweites Druckfeld erzeugt wird, das dem ersten Druckfeld entgegenwirkt, das von der von der Druckmittelquelle belasteten Ausnehmung erzeugt wird. Das Druckfeld wird auf der dem Spritzverstell-Kolben gegenüberliegenden Seite durch den im Gehäuse der Kraftstoffeinspritzpumpe gelagerten Kupplungsteil des Nockensantriebs abgefangen.In an advantageous embodiment, closes according to claim 4 the coupling part in the recess in the injection piston a pressure room in which a second pressure field is generated, which counteracts the first pressure field, the from the recess loaded by the pressure medium source is produced. The pressure field is on the the injection piston opposite side through the in the housing of the Fuel injection pump mounted coupling part of the Intercepted cam drive.

Eine weitere vorteilhafte Ausgestaltung der Erfindung besteht darin, daß gemäß Patentanspruch 6 zwischen der Mantelfläche des Spritzverstell-Kolbens und der Wand des Zylinders eine zusätzliche Ausnehmung vorgesehen ist in deren Bereich das zweite Druckfeld gebildet ist, das kompensierend auf die durch das erste Druckfeld und die vom Nockenantrieb bewirkten Kippmomente wirkt. Diese Ausführung bedarf eines zusätzlichen konstruktiven Aufwandes gegenüber der vorstehend genannten Ausgestaltung, ist jedoch im Bezug auf die bei der erstgenannten Ausgestaltung notwendige Abdichtung des Druckraumes unproblematischer.Another advantageous embodiment of the invention is that according to claim 6 between the Shell surface of the injection piston and the wall of the An additional recess is provided in the cylinder whose area the second pressure field is formed, the compensating for that from the first pressure field and from the The tilting moment caused by the cam drive acts. This execution requires an additional constructive effort the above configuration, but is related to the necessary in the first-mentioned configuration Sealing the pressure chamber is less problematic.

Vorteilhaft werden die Ausnehmung und die zusätzliche Ausnehmung jeweils als Längsschlitz ausgeführt und liegen in einem gemeinsamen Ringbereich der Mantelfläche des Spritzverstell-Kolbens. The recess and the additional are advantageous Recess made as a longitudinal slot and are in a common ring area of the lateral surface of the Spritzverstell flask.

Eine andere vorteilhafte Ausgestaltung der Erfindung besteht gemäß Patentanspruch 11 darin, beiderseits des Kupplungsteils Stellen an dem den Spritzverstell-Kolben führenden Zylinder vorzusehen, die jeweils ein zweites Druckfeld zur Kompensation des ersten Druckfeldes und der Momente, denen der Spritzverstell-Kolben ausgesetzt ist, erzeugen. Vorteilhaft wird dabei gemäß Patentanspruch 12 der Spritzverstell-Kolben in einer in das Gehäuse der Kraftstoffeinspritzpumpe eingesetzten Zylinderhülse aus verschleißfestem Werkstoff geführt. Dies gewährt optimale Gleiteigenschaften zwischen Spritzverstell-Kolben und der Zylinderhülse und eine Sicherheit gegen Versagen. Vorteilhaft und mit geringerem Herstellungsaufwand kann dabei ferner die Verbindung zwischen den der Ausnehmung im wesentlichen gegenüberliegenden Stellen zwischen der Mantelfläche des Spritzverstell-Kolbens und der Wand des Zylinders dadurch realisiert werden, daß die zu diesen Stellen führenden Verbindungskanäle zwischen der Zylinderhülse und dem Gehäuse als Rinnen eingearbeitet sind. Zur Verbesserung der Abdichtung des vom Spritzverstell-Kolben im Zylinder eingeschlossenen Arbeitsraumes weist dieser einen metallischen, sich elastisch an die innere Mantelfläche des Zylinders bzw. der Zylinderhülse anlegenden Dichtring auf. Damit ist auch in den Bereichen des Spritzverstell-Kolbens, die keinen so hohen radialen Kräften ausgesetzt ist, die Abdichtung des Arbeitsraumes gewährleistet.Another advantageous embodiment of the invention exists according to claim 11 therein, on both sides of the Coupling part places on the injection adjustable piston to provide leading cylinders, each a second Pressure field to compensate for the first pressure field and the Moments to which the spray adjustment piston is exposed produce. According to claim 12, the Injection-adjustable pistons in one in the housing of the Fuel injection pump inserted cylinder sleeve wear-resistant material. This grants optimal Sliding properties between the injection adjustable piston and the Cylinder sleeve and security against failure. Can be advantageous and with less manufacturing effort the connection between the recess in the essential opposite points between the Shell surface of the injection piston and the wall of the Cylinder can be realized in that the to these Make leading connection channels between the Cylinder sleeve and the housing are incorporated as gutters. To improve the sealing of the injection adjustable piston working space enclosed in the cylinder has this one metallic, elastic to the inner Apply the outer surface of the cylinder or the cylinder sleeve Sealing ring on. This is also in the areas of Injection-adjusting pistons that do not have such high radial forces is exposed, the sealing of the work area guaranteed.

Zeichnungdrawing

Vier Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und werden in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 ein erstes Ausführungsbeispiel der Erfindung mit einem vom Kupplungsteil und Spritzverstellerkolben eingeschlossenen Drckraum zur Bereitstellung eines kompensierenden zweiten Druckfeldes, Figur 2 einen Längsschnitt durch das Ausführungsbeispiel nach Figur 1 entlang der Linie II-II in Figur 1 mit einer zweiten Ausführungsform der Erfindung unter Einsatz einer kompensierende Druckfeder, Figur 3 ein drittes Ausführungsbeispiel der Erfindung, dargestellt in Form eines Längsschnittes durch einen Spritzverstellerkolben der Kraftstoffeinspritzpumpe, Figur 4 einen Schnitt durch das Ausführungsbeispiel gemäß Figur 3 entlang der Linie IV-IV von Figur 3, Figur 5 ein viertes Ausführungsbeispiel der Erfindung anhand eines Längsschnittes durch einen Spritzverstell-Kolben mit einer ersten Variante der Führungen der Verbindungskanäle und Figur 6 eine Abwandlung des Ausführungsbeispiels nach Figur 5 mit einer zweiten Variante der Verbindungskanäle, gezeigt an einem Zylinder, bei dem die Zylinderhülse gemäß Figur 5 und der Spritzverstellerkolben noch nicht montiert sind.Four embodiments of the invention are in the Drawing and are shown in the following Description explained in more detail. 1 shows a first Embodiment of the invention with one of Coupling part and injection adjuster piston included Pressure space to provide a compensating second Pressure field, Figure 2 shows a longitudinal section through the Embodiment according to Figure 1 along the line II-II in Figure 1 with a second embodiment of the invention using a compensating compression spring, Figure 3 a third embodiment of the invention, shown in Shape of a longitudinal section through an injection piston the fuel injection pump, Figure 4 shows a section through the embodiment of Figure 3 along the line IV-IV of Figure 3, Figure 5 shows a fourth embodiment of the Invention based on a longitudinal section through a Injection-adjustable pistons with a first variant of the Guides of the connecting channels and Figure 6 a modification of the embodiment of Figure 5 with a second Variant of the connection channels, shown on a cylinder, in which the cylinder sleeve according to Figure 5 and the Spray adjuster pistons are not yet installed.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Kraftstoffeinspritzpumpen der Verteilerbauart können entweder als Pumpen mit einem sowohl als Verteiler als auch Pumpenkolben dienenden, axial angetriebenen Pumpenkolben versehen werden, oder es können Radialkolben vorgesehen werden, die radial in in einem Verteiler angeordneten Förderkanal fördern. In beiden Fällen werden die Pumpenkolben durch einen von der Antriebswelle der Kraftstoffeinspritzpumpe bewegten Nockenantrieb betätigt. Ein Teil einer solchen sogenannte Radialkolbenpumpe ist im Schnitt in Figur 1 dargestellt. Bei solchen Pumpen werden z. B. vier, hier nicht gezeigte Pumpenkolben vorgesehen, die in im gleichen Winckelabstand zueinander gemeinsam radial zur Achse des Verteilers hin verlaufenden Radialbohrungen im Verteiler dicht verschiebbar gelagert sind. Auf ihrer einen Stirnseite schließen sie einen gemeinsamen Pumpenarbeitsraum ein, der in bekannter Weise beim Radialauswärtshub der Pumpenkolben mit Kraftstoff gefüllt wird und beim Radialeinwärtshub der Pumpenkolben über eine Druckleitung mit einer Verteileröffnung an der Mantelfläche des Verteilers verbunden wird, wobei die Verteileröffnung am Umfang des Verteilers abgehende Einspritzleitungen ansteuert, von denen jeweils eine beim Einwärtsbewegen der Pumpenkolben mit auf Einspritzdruck gebrachtem Kraftstoff versorgt wird. Der Verteiler wird von einer Antriebswelle rotierend angetrieben derart, daß einerseits die Verteileröffnung ihre Steuerfunktion ausführen kann und andererseits die Pumpenkolben in Umfangsrichtung entlang einer Nnockenbahn bewegt werden. Diese Konstruktion ist hier nicht näher gezeigt, da sie als allgemein bekannt vorausgesetzt wird. Gezeigt ist ein Teil der Nockenbahn 2, die auf der Innenseite eines Nockenrings 3 angeordnet ist und der die Pumpenkolben folgen. Der Nockenring 3 stellt den im wesentlichen stillstehenden Teil des Nockenantriebs der Pumpenkolben dar. Während die die Pumpenkolben bewegende Einrichtung, die z. B. der die Rollenstößel führende Ring oder Verteiler sein kann, der mit der Antriebswelle gekoppelt ist, den bewegten Teil des Nockenantriebs darstellt. Der Nockenring ist mit seinem Außenumfang in einer zylindrischen Ausnehmung 5 im Gehäuse 6 der Kraftstoffeinspritzpumpe gelagert und kann in einer Ebene senkrecht zur Antriebsachse der Kraftstoffeinspritzpumpe verdreht werden. Durch die Drehstellung des Nockenrings läßt sich nun bezogen auf die Antriebsbewegung des Verteilers der Zeitpunkt des jeweiligen Förderhubbeginns der Pumpenkolben verändern. Zur Verdrehung weist der Nockenring 3 ein Kupplungsteil in Form eines einstückig von diesem radial nach außen abstehenden Zapfens 7 auf, der in eine Vertiefung 9 eines Spritzverstell-Kolbens 10 eintaucht. Fuel injection pumps of the distributor type can either as pumps with one as both distributor and Pump piston serving, axially driven pump piston can be provided, or radial pistons can be provided are arranged radially in a manifold Promote the delivery channel. In both cases, the Pump piston through one of the drive shaft of the Fuel injection pump actuated moving cam drive. Part of such a so-called radial piston pump is in the Section shown in Figure 1. In such pumps, for. B. four pump pistons, not shown here, provided in at the same angular distance from each other together radially to Radial bores in the axis of the distributor Distributors are mounted tightly displaceable. On her one At the end, they close a common pump work room a, which is known in the radial outward stroke of the Pump piston is filled with fuel and at Radial inward stroke of the pump pistons via a pressure line with a distributor opening on the lateral surface of the Distributor is connected, the distributor opening on Scope of the distributor outgoing injection lines controls, of which one each when moving the Pump piston with fuel brought up to injection pressure is supplied. The distributor is driven by a drive shaft rotatably driven such that the one hand Distributor opening can perform its control function and on the other hand, the pump pistons along the circumferential direction a cam track can be moved. This construction is here not shown in detail since it is generally known is assumed. Part of cam track 2 is shown, which is arranged on the inside of a cam ring 3 and which the pump pistons follow. The cam ring 3 represents the essentially stationary part of the cam drive Pump piston represents. While the moving the pump piston Facility that z. B. the ring leading the roller tappet or distributor that can be with the drive shaft is coupled, the moving part of the cam drive represents. The outer circumference of the cam ring is in a cylindrical recess 5 in the housing 6 of the Fuel injection pump stored and can be in one level perpendicular to the drive axis of the fuel injection pump be twisted. By turning the cam ring now refer to the drive movement of the distributor of Time of the beginning of the delivery stroke of the pump piston change. The cam ring 3 has a torsion Coupling part in the form of an integral part of this radially outwardly projecting pin 7, which in a recess 9 of an injection adjusting piston 10 is immersed.

Der Spritzverstell-Kolben ist in einem Zylinder 11 dicht verschiebbar und schließt mit seiner einen Stirnseite 12 mit dem geschlossenen Ende des Zylinders 11 einen Arbeitsraum 14 ein und mit seiner anderen Stirnfläche im dort ebenfalls verschlossenen Zylinder 11 einen Federraum 15 ein. In diesem ist eine Rückstellfeder 16 angeordnet, die sich einerseits an einem dem Zylinder verschließenden Verschlußteil 17 und andererseits an der Stirnseite 19 des Spritzverstell-Kolbens 10 abstützt und so eingespannt bestrebt ist, den Spritzverstell-Kolben mit seiner einen Stirnseite 12 in Anlage an die den Zylinder 11 gegenüberliegend verschließende Wand 20 oder einen dort angeordneten Anschlag zu bringen.The spray adjustment piston is sealed in a cylinder 11 displaceable and closes with its one end face 12 the closed end of the cylinder 11 a working space 14 one and with its other end face in there as well closed cylinder 11 a spring chamber 15. In this a return spring 16 is arranged, the one hand on a closing part 17 and on the other hand, on the end face 19 of the injection adjustment piston 10 supports and strives so clamped, the Injection-adjusting piston with one end face 12 in Facing the cylinder 11 opposite closing wall 20 or a stop arranged there bring to.

Im Spritzverstell-Kolben 10 ist ferner eine Zylinderbohrung 22 vorgesehen, in Form einer axialen Sackbohrung, die von der Stirnseite 19 ausgeht. Ein dort eingesetzter Steuerschieber 24 schließt mit seiner einen Stirnseite 25 mit dem geschlossenen Ende der Sackbohrung einen druckentlasteten Endraum ein, in dem eine Druckfeder 27 eingespannt ist, die den Steuerschieber 24 auf dieser Stirnseite 25 belastet und ihm mit seinem anderen Ende in Anlage an einem Stößel 28 hält, der in den Federraum 15 eintaucht. Dieser Stößel weist dort einen Federteller 29 auf, an dem sich eine Steuerfeder 30 abstützt, die sich andererseits am Verschlußteil 17 abstützt. Der Stößel ist in einer Bohrung 31 des Verschlußteils 17 geführt und ragt in einen Zylinder 32, der innerhalb des Verschlußteils 17 angeordnet ist. Dort geht der Stößel in einen Kolben 33 über, der dicht in dem Zylinder gleitet und federraumseitig zusammen mit dem Stößel einen Arbeitsraum 34 einschließt, der über eine Bohrung 35 mit Druckmittel versorgt wird. Dieses Druckmittel wird auf einen Steuerdruck gehalten, der im wesentlichen drehzahlabhängig ist, aber auch in Abhängigkeit von anderen Parametern der Brennkraftmaschine variiert werden kann, wie z. B. in Abhängigkeit von der Last. Der Druck wird in einer Steuerdruckquelle, die hier nicht weiter dargestellt ist, in bekannter Weise bereitgestellt. Bei Druckerhöhung im Arbeitsraum 34 wird der Stößel zusammen mit dem Kolben 33 gegen die Kraft der Steuerfeder 30 verschoben. Dieser Verschiebung folgt gestützt durch die Druckfeder 27 der Steuerschieber 24.There is also a cylinder bore in the injection adjustment piston 10 22 provided in the form of an axial blind bore, which by the end face 19 goes out. One used there Control slide 24 closes with its one end face 25 with the closed end of the blind hole pressure-relieved end space in which a compression spring 27 is clamped, the spool 24 on this Face 25 loaded and him with his other end in Holds on a plunger 28 which in the spring chamber 15th dips. This plunger has a spring plate 29 there on which a control spring 30 is supported, which on the other hand is supported on the closure part 17. The pestle is in a bore 31 of the closure member 17 out and protrudes in a cylinder 32, which is inside the closure part 17th is arranged. There the plunger goes into a piston 33 above, which slides tightly in the cylinder and on the spring chamber side includes a working space 34 together with the ram, which is supplied with pressure medium via a bore 35. This pressure medium is kept at a control pressure which is essentially speed-dependent, but also in Dependence on other parameters of the internal combustion engine can be varied, such as. B. depending on the Load. The pressure is in a control pressure source, which is here is not shown in a known manner provided. When the pressure in the work space 34 increases Ram together with the piston 33 against the force of Control spring 30 moved. This shift follows supported by the compression spring 27 of the control slide 24.

Die koaxial und parallel zur Rückstellfeder 16 im Federraum 15 angeordnete Steuerfeder 30 ist von Kraftstoff umspült, der als Leckmenge oder Absteuermenge aus dem Federraum 15 einem Entlastungsraum zugeführt wird. Mit dem Federraum 15 ist auch der andererseits des Kolbens 33, im Zylinders 32 eingeschlossene Raum 38 verbunden und zwar über eine Axialbohrung 36 im Stößel 28, die über eine Radialbohrung 37 ihren Austritt am Stößel innerhalb des Federraums 15 hat.The coaxial and parallel to the return spring 16 in the spring chamber 15 arranged control spring 30 is flushed with fuel, of the leakage or discharge amount from the spring chamber 15 a relief room is supplied. With the spring chamber 15 is also that of the piston 33 in the cylinder 32 enclosed space 38 connected via a Axial bore 36 in the plunger 28, which has a radial bore 37 has its exit on the tappet within the spring chamber 15.

Der Steuerschieber 24 weist drei dicht nebeneinander liegende Ringbünde auf, von denen ein erster Ringbund 39, der federraumseitig liegt eine federraumseitige Steuerkante 40 aufweist, über die ein hier in der Zeichnung nicht gezeigter, von der axialen Sackbohrung 22 zum Arbeitsraum 14 führender Entlastungskanal 41 bei einer bestimmten Relativstellung von Steuerschieber 24 und Spritzverstell-Kolben 10 zueinander zum Federraum 15 hin geöffnet wird. Dieser Entlastungskanal 41 ist in der Figur 2 gezeigt.The control slide 24 has three close to each other lying ring bundles, of which a first ring bundle 39, the spring chamber side has a control edge on the spring chamber side 40, about which not one here in the drawing shown, from the axial blind bore 22 to the working space 14 leading relief channel 41 at a particular Relative position of control spool 24 and spray-adjusting piston 10 is opened towards each other towards the spring chamber 15. This relief channel 41 is shown in FIG. 2.

Zur Seite des Arbeitsraumes 14 folgt dem ersten Ringbund 39 ein zweiter Ringbund 43, der der Führung des Steuerschiebers dient und zugleich der Milderung eines Druckentlastungsstoßes. Diesem Ringbund 43 folgt dann ein dritter Ringbund 45, der zur Seite des Arbeitsraumes 14 eine Steuerkante 46 aufweist, über die ein von der axialen Sackbohrung ausgehender Füllkanal 48, der über ein Rückschlagventil 49 in den Arbeitsraum 14 mündet, gesteuert wird. Stellt diese Steuerkante die Verbindung zwischen dem Austritt 50 des Füllkanals 48 mit einer sich zur Seite des Arbeitsraumes 14 an die Steuerkante anschließenden Ringnut 51 her, so wird dadurch aus dieser Ringnut Kraftstoff unter Steuerdruck, der zugleich auch Betätigungsdruck ist, über den Füllkanal in den Arbeitsraum 14 gleitet. Die Ringnut ist ständig über einen Zuflußkanal 53 mit einer Ausnehmung 54 in der Mantelfläche des Spritzverstell-Kolbens verbunden. Die als Längsnut längs einer Mantellinie des Spritzverstell-Kolbens ausgebildete Ausnehmung ist in ständiger Verbindung mit einem Druckmittelzulauf 55, der vorzugsweise von der Steuerdruckquelle herführt, die auch den Arbeitsraum 34 versorgt. Die Zuordnung dieser Lägnsnut zur Einmündung des Druckmittelzulaufes 55 in den Zylinder ist durch die Koppelung des Spritzverstell-Kolbens 10 mit dem Zapfen 7 des Nockenringes gewährleistet. In Figur 2 ist die Lage dieser Längsnut 54 entnehmbar, die symbolisch in Figur 1 nur gestrichelt eingezeichnet ist.The first ring collar 39 follows the side of the working space 14 a second collar 43, which is the control of the spool serves and at the same time the mitigation of a pressure relief surge. This ring collar 43 is then followed by a third ring collar 45, a control edge 46 to the side of the working space 14 has one of the axial blind bore outgoing filling channel 48, which via a check valve 49 opens into the work space 14, is controlled. Provides this Control edge the connection between the outlet 50 of the Filling channel 48 with one to the side of the working space 14 to the control edge ring groove 51 forth, so thereby fuel from this annular groove under control pressure at the same time there is actuating pressure via the filling channel in the work space 14 slides. The ring groove is constantly over an inflow channel 53 with a recess 54 in the The outer surface of the spray adjustment piston is connected. As Longitudinal groove along a surface line of the injection adjustment piston trained recess is in constant communication with a pressure medium inlet 55, which is preferably from the Control pressure source that also produces the work space 34 provided. The assignment of this Lägnsnut to the confluence of the Pressure medium inlet 55 in the cylinder is through the Coupling the Spritzverstell-piston 10 with the pin 7 of Guaranteed cam ring. The position of this is in FIG Longitudinal groove 54 can be removed, the symbolic in Figure 1 only is shown in dashed lines.

Diese Ausführung des Spritzbeginnverstellers mit dem Spritzverstell-Kolben 10 arbeitet so, daß bei einer Erhöhung des Steuerdrucks der Kolben 33 gegen die Kraft der Steuerfeder 30 nach rechts verschoben wird und sich der Steuerschieber 24 demzufolge auch nach rechts bewegt. Ausgehend von der gezeigten Position in Figur 1 öffnet dann der Steuerschieber mit der Steuerkante 46 die Verbindung zwischen Füllkanal 48 und Ringnut 51 bzw. Druckmittelzulauf 55. Es fließt zusätzliches Druckmittel über das Rückschlagventil 49 in den Arbeitsraum 14, was wiederum bewirkt, daß der Spritzverstell-Kolben 10 gegen die Kraft der Rückstellfeder 16 nach rechts verschoben wird so lange, bis die Mündung 50 des Füllkanals 48 durch die Steuerkante 46 wieder verschlossen ist. Im dazwischenliegenden Bereich kann der Spritzverstell-Kolben 10 weiter nach rechts verschoben werden, ohne daß eine Verbindung zwischen Arbeitsraum 14 und Druckmittelzulauf 55 bzw. Federraum 15 und Entlastungsraum auftritt. Die Mündung 15 wird vielmehr bei Erreichen des zweiten Ringbundes nochmals abgedichtet und erst wenn sich dann der Steuerschieber nach links aufgrund einer Druckentlastung im Arbeitsraum 34 bewegt, wird dann der hier nicht gezeigte Entlastungskanal geöffnet. Der Federraum 15 und der Endraum der axialen Sackbohrung sind über eine Leitung 56 miteinander verbunden, so daß der Steuerschieber beidseitig hydraulisch druckausgeglichen ist.This version of the spray start adjuster with the Spritzverstell-piston 10 works so that with an increase of the control pressure of the piston 33 against the force of the Control spring 30 is moved to the right and the Control slide 24 consequently also moved to the right. Starting from the position shown in Figure 1 then opens the control slide with the control edge 46 the connection between filling channel 48 and annular groove 51 or pressure medium inlet 55. Additional pressure medium flows over the Check valve 49 in the work space 14, which in turn causes the Spritzverstell piston 10 against the force the return spring 16 is shifted to the right as long as until the mouth 50 of the filling channel 48 through the control edge 46 is closed again. In the area in between can the spray adjustment piston 10 further to the right be moved without a connection between Work chamber 14 and pressure medium inlet 55 or spring chamber 15 and relief space occurs. The mouth 15 is rather sealed again when reaching the second ring collar and only when the control spool turns to the left moved due to a pressure relief in the work space 34, the relief channel, not shown here, is then opened. The spring space 15 and the end space of the axial blind bore are connected via a line 56 so that the Control valve is hydraulically pressure balanced on both sides.

Die Vertiefung 9 in der Mantelfläche des Spritzverstell-Kolbens ist im Querschnitt jeweils kreisförmig, so daß der Zapfen 7 in dieser Vertiefung einen Druckraum 57 einschließt. Dieser Druckraum steht über eine kurze Bohrung 58 in ständiger Verbindung mit der Ringnut 51 und ist dem Steuerdruck ausgesetzt.The recess 9 in the outer surface of the injection piston is circular in cross section, so that the Pin 7 a pressure chamber 57 in this recess includes. This pressure chamber has a short bore 58 in constant connection with the ring groove 51 and is the Tax pressure exposed.

Im Bereich des Eintritts des Zapfens 7 in die Vertiefung besitzt das Gehäuse 6 eine den Innenraum 4 der Kraftstoffeinspritzpumpe mit dem Zylinder 11 verbindende Ausnehmung 60 derart, daß der Zapfen 7 den Verstellbewegungen des Spritzverstell-Kolbens 10 ungehindert folgen kann. In diesem Bereich ist die Mantelfläche des Spritzverstell-Kolbens 10 einem niedrigen Innenraumdruck der Kraftstoffpumpe ausgesetzt, der in der Größenordnung des Entlastungsdruckes liegt, den Spritzverstell-Kolben also nicht wesentlich radial belastet.In the area of the entry of the pin 7 into the recess the housing 6 has an interior 4 of the Fuel injection pump with the cylinder 11 connecting Recess 60 such that the pin 7 the Adjustment movements of the spray adjustment piston 10 unimpeded can follow. In this area, the outer surface of the Spritzverstell-piston 10 a low interior pressure Fuel pump exposed to the order of magnitude Relief pressure is, so the injection piston not significantly loaded radially.

Damit der Spritzverstell-Kolben bei den hohen auf ihn wirkenden Kräften möglichst verschleißarm geführt werden kann unter Berücksichtigung der Tatsache, daß das Gehäuse 6 der Einspritzpumpe beispielsweise aus Aluminiumdruckguß besteht, ist als Zylinder eine Zylinderhülse 61 vorgesehen, die aus hochwertigem Stahl besteht und in eine entsprechende zylindrische Bohrung des Gehäuses eingesetzt bzw. eingepreßt ist. Der Spritzverstell-Kolben selber besteht ebenfalls aus hochwertigem Stahl, der dazu noch eine entsprechende Oberflächenvergütung zur Anhebung der Verschleißfestigkeit aufweisen kann. Weiterhin ist für eine dichte Führung des Spritzverstell-Kolbens insbesondere auf der Seite des Arbeitsraumes 14 in die Mantelfläche des Spritzverstell-Kolbens 10 eine Ringnut 63 eingearbeitet, in die ein metallischer Kolbenring 64 gesetzt ist, der eine hochwertige Abdichtung gewährleistet.So that the injection piston at the high on it acting forces are carried out with as little wear as possible can take into account the fact that the housing 6 the injection pump, for example made of die-cast aluminum there is a cylinder sleeve 61 provided as a cylinder, which is made of high quality steel and in a corresponding cylindrical bore of the housing inserted or pressed is. The injection adjustment piston itself also consists of high quality steel, which also has a corresponding Surface coating to increase wear resistance can have. Furthermore, for a tight management of the Spritzverstell-Pistons especially on the side of the Working space 14 in the outer surface of the injection piston 10 an annular groove 63 incorporated into the metallic piston ring 64 is set, which is a high quality Sealing guaranteed.

Der Spritzverstell-Kolben 10 und der Kolben 33 nebst Stößel 28 und Federn 16 und 30 benötigen einen bestimmten Bauraum. Dabei beansprucht der außerhalb des Spritzverstell-Kolbens 10 liegende Stellkolben bestehend aus Stößel und Kolben 33 gegenüber anderen Ausführungen eines Spritzverstellers einen zusätzlichen Raum. Der Spritzverstell-Kolben ist auf der Seite des Federraumes 15 aus diesem Grunde kürzer gehalten, damit gewisse vorgegebene Baumaße des Spritzverstellers beibehalten werden können. Der Steuerschieber erstreckt sich deshalb aus Platzersparnisgründen insbesondere auch über den Bereich, an dem der Nockenring 3 über den Zapfen 7 mit dem Spritzverstell-Kolben 10 gekoppelt ist. Dies bedingt wiederum einen exzentrischer Angriff des Zapfens 7 am Spritzverstell-Kolben und unter Belastung einer axial anzusetzenden Längskraft, resultierend aus dem Druck im Arbeitsraum 14 und einer vom Nockenring 3 übertragenen Rückstellkraft, ergibt sich zwischen dem Angriffspunkt des Zapfens 7 am Spritzverstell-Kolben 10 und der Achse des Spritzverstell-Kolbens 10 ein Hebelarm, der zusammen mit diesen Kräften ein Kippmoment auf den Spritzverstell-Kolben ausübt. Diesem müssen durch Auflagekräfte Rückhaltemomente entgegengesetzt werden. Zudem ist der Spritzverstell-Kolben durch das in der Zeichnung unten liegende bzw. bezogen auf Figur 2 im wesentlichen unten liegende, Druckfeld belastet, was die Auflagekräfte FA und FB, die hier repräsentativ punktförmig eingezeichnet wurden, erhöhen. Das Druckfeld, das als erstes Druckfeld von der Längsnut 54 ausgeht, ist in der Figur 2 als erstes Druckfeld 66 schematisch dargestellt. Es erhöht zusammen mit den Auflagekräften, die aus dem Kippmoment resultieren, die Flächenpressung auf der Seite des Nockenrings zwischen Spritzverstell-Kolben 10 und Zylinder 11. Erhöhte Kräfte in Verbindung mit Materialeigenschaften und Rauhigkeiten der Materialpaarungen können zum Versagen des Bauteils führen.The spray adjustment piston 10 and the piston 33 together with the plunger 28 and springs 16 and 30 require a certain amount of space. The load outside of the injection adjustment piston 10 horizontal actuating pistons consisting of tappet and piston 33 compared to other versions of a spray adjuster additional space. The spray adjustment piston is on the Side of the spring chamber 15 is kept shorter for this reason, thus certain predetermined dimensions of the spray adjuster can be maintained. The spool extends therefore, in order to save space, in particular via the Area where the cam ring 3 over the pin 7 with the Injection adjustment piston 10 is coupled. This requires again an eccentric attack on the pin 7 on Injection-adjustable pistons and under axial load longitudinal force to be applied, resulting from the pressure in the Working space 14 and one transmitted from the cam ring 3 Restoring force results between the point of application of the Pin 7 on the injection piston 10 and the axis of the Spritzverstell-piston 10 a lever arm, which together with these forces a tipping moment on the spray adjustment piston exercises. This must be withheld by support forces be opposed. In addition, the injection adjustable piston by the one in the drawing below or related to FIG. 2 shows the pressure field lying essentially at the bottom, what the support forces FA and FB, which are representative here were drawn in punctiform. The pressure field, that emerges from the longitudinal groove 54 as the first pressure field is shown in 2 schematically shown as the first pressure field 66. It increases along with the tracking forces that come from the Tipping moment result, the surface pressure on the side of the cam ring between the injection piston 10 and Cylinder 11. Increased forces in connection with Material properties and roughness of the material pairings can lead to component failure.

Dadurch, daß nun in dem Druckraum 57 der Steuerdruck eingeführt wird, ergibt sich dort ein zweites Druckfeld, das dem ersten Druckfeld und den Kippkräften zum Teil entgegenwirkt. Auf diese Weise kann die Radialbelastung des Spritzverstell-Kolbens wesentlich verringert werden, ohne daß wesentliche konstruktive Änderungen am Spritzverstell-Kolben notwendig werden. Es ist lediglich dafür zu sorgen, daß der Zapfen 7 den Druckraum 57 relativ dicht einschließt, dabei wirkt der Zapfen mit seiner Stirnseite in Verbindung mit der Lagerung des Nockenrings 3 als Stützfläche. Aufgrund der Längsbewegung des Spritzverstell-Kolbens 10 ist die Verbindungspaarung zwischen Zapfen 7 und Vertiefung 9 derart auszulegen, daß auch leichte Schwenkbewegungen des Zapfens relativ zum Spritzverstell-Kolben 10 durchgeführt werden können. Vorzugsweise ist der Zapfen an der Verbindungsstelle zum Spritzverstell-Kolben 10 kugelig ausgebildet. Um auch hier den Verschleiß niedrig zu halten, sind die Teile, die hier einander berühren, gehärtet. Insbesondere ist auch der Spritzverstell-Kolben 10 aus Verschleißgründen einsatzgehärtet.Because now in the pressure chamber 57 the control pressure is introduced, there is a second pressure field there the first pressure field and the tipping forces in part counteracts. In this way, the radial load on the Injection plunger piston can be significantly reduced without that significant design changes to the injection-adjustable piston become necessary. You just have to make sure that the pin 7 encloses the pressure chamber 57 relatively tightly, the peg acts in connection with its end face with the bearing of the cam ring 3 as a support surface. by virtue of the longitudinal movement of the injection piston 10 is the Connection pair between pin 7 and recess 9 in such a way interpret that even slight pivoting movements of the pin be carried out relative to the spray adjustment piston 10 can. The pin is preferably at the connection point for spherical injection-adjustable piston 10. Too keeping the wear down here are the parts that touch each other here, hardened. In particular, the Injection-adjusting piston 10 for reasons of wear casehardened.

Statt eines hydraulisch erzeugten Druckfeldes im Bereich der Ausnehmung 57 kann dieses zweite Druckfeld durch eine Gegenkraft realisiert werden, die durch eine zwischen Zapfen 7 und Ausnehmung 57 eingespannte Druckfeder 76 erzeugt wird, wie in Figur 2 gezeigt.Instead of a hydraulically generated pressure field in the area of Recess 57 can this second pressure field through a Counterforce can be realized by a between pin 7 and recess 57 clamped compression spring 76 is generated, as shown in Figure 2.

In weiterer Abwandlung zum Ausführungsbeispiel nach Figur 1 wird gemäß der Ausführung nach Figur 3 das zweite Druckfeld, das in dem Druckraum 57 realisiert war, in Form einer zusätzlichen Längsnut 67 in der Mantelfläche des Spritzverstell-Kolbens realisiert. Der Kolben und sein Antrieb sind dabei, wie in Figur 3 gezeigt, im wesentlichen gleich aufgebaut, wie beim Ausführungsbeispiel nach Figur 1. Es kann somit auf die diesbezügliche Beschreibung dieser Figur verwiesen werden. Der Schnitt nach Figur 3 zeigt jedoch eine Ansicht, die sich aus dem Schnitt III-III von Figur 4 ergibt. Der Figur 4 entnimmt man, daß die zusätzliche Längsnut 67 im wesentlichen diametral der Längsnut 54 gegenüberliegt. Die Verbindung zwischen der Ringnut 51 und dieser zusätzlichen Längsnut 67 erfolgt über eine Verbindungsleitung 68. Das sich an der zusätzlichen Längsnut 67 aufbauende zweite Druckfeld ist dabei dem sich an der Längsnut 54 aufbauenden Druckfeld gleichwertig. Somit heben sich die aus diesen Druckfeldern entstehende Kräfte auf, so daß die Radialbelastung des Spritzverstell-Kolbens 10 wesentlich verringert ist.
Es ist weiterhin vorteilhaft, wenn die Druckfelder eindeutig dimensioniert werden können, um den erwünschten Druckausgleich genau einzustellen. Dazu sind im geringen abstand und parallel zu den Längsnute 67 und 54 auf der der Vertiefung 9 abgewandten Seite je eine zusätzliche Rille 71 72 vorgesehen, die länger als diese Nuten 67 und 54 sind und diese beidseitig überragend mit ihrem einen Ende in den Federraum 15 münden. Somit wird das Druckfeld jeweils an der Stelle der zusätzlichen Rillen zum Federraum hin entlastet und so in Umfangsrichtung begrenzt. In a further modification to the exemplary embodiment according to FIG. 1, the second pressure field, which was realized in the pressure chamber 57, is realized in the form of an additional longitudinal groove 67 in the lateral surface of the injection-adjusting piston according to the embodiment according to FIG. As shown in FIG. 3, the piston and its drive are constructed essentially the same as in the exemplary embodiment according to FIG. 1. Reference can therefore be made to the description of this figure in this regard. However, the section according to FIG. 3 shows a view that results from section III-III of FIG. 4. It can be seen from FIG. 4 that the additional longitudinal groove 67 lies essentially diametrically opposite the longitudinal groove 54. The connection between the annular groove 51 and this additional longitudinal groove 67 takes place via a connecting line 68. The second pressure field building up on the additional longitudinal groove 67 is equivalent to the pressure field building up on the longitudinal groove 54. The forces arising from these pressure fields thus cancel each other out, so that the radial load on the injection-adjusting piston 10 is substantially reduced.
It is also advantageous if the pressure fields can be clearly dimensioned in order to precisely set the desired pressure compensation. For this purpose, an additional groove 71 72 is provided at a short distance and parallel to the longitudinal grooves 67 and 54 on the side facing away from the recess 9, which are longer than these grooves 67 and 54 and projecting on both sides with one end projecting into the spring chamber 15 , Thus, the pressure field is relieved to the spring space at the location of the additional grooves and thus limited in the circumferential direction.

Figur 5 zeigt weiterhin ein drittes Ausführungsbeispiel für eine Entlastung des Spritzverstell-Kolbens 10 von schädlichen Radialkräften. Auch diese Ausführung basiert auf der Bereitstellung eines zweiten Druckfeldes, das dem ersten Druckfeld entgegengerichtet ist, hierbei ist dieses jedoch in zwei zweite Druckfelder aufgeteilt, um möglichst alle am Spritzverstell-Kolben 10 auftretenden Momente zu erfassen. Auch hier ist der Spritzverstell-Kolben mit Steuerschieber in gleicher Weise aufgebaut wie bei dem Ausführungsbeispiel nach Figur 1 und 3, so daß eine diesbezügliche ergänzende Beschreibung nicht notwendig ist. Abweichend von dem Ausführungsbeispiel nach Figur 1 sind nun zwischen der Zylinderhülse 61 und dem angrenzenden Gehäuse 6 der Kraftstoffeinspritzpumpe ein erster Verbindungskanal 69 und ein zweiter Verbindungskanal 70 vorgesehen, die von dem Druckmittelzulauf 55 ausgehend zunächst parallel zu einer Mantellinie der Zylinderhülse 61 verlaufen und dann jeweils in eine Halbringnut 72 bzw. 73 übergehen, die zu einer Stelle am Umfang der Zylinderhülse 61 führen, die diametral zum Eintritt des Druckmittelzulaufes 55 in den Zylinder 11 liegen. Dort weist die Zylinderhülse jeweils einen ersten Durchbruch 75 und einen zweiten Durchbruch 74 auf, über die die Verbindungskanäle 69 bzw. 70 Verbindung zum Innern des Zylinders 11 haben im Bereich zwischen Zylinder 11 und Mantelfläche des Spritzverstell-Kolbens. In diesem Bereich bauen sich zweite Druckfelder auf, die in der Zeichnung symbolich als Fda symbolisiert sind. Diese Kräfte liegen dabei symmetrisch zur Mittellinie des Zapfens 7 damit sie für einen gleichmäßigen Kräfteausgleich am Spritzverstell-Kolben 10 sorgen. Sie wirken den resultierenden Auflagekräften FA und FB, die aus der Belastung des ersten Druckfeldes im Bereich des Druckmittelzulaufes 55 resultieren, entgegen. Sie wirken zudem auch zumindestens einer Kraftkomponente der vom Kippmoment auf dem Stellkolben ausübenden Kippkräfte entgegen. Mit der Bereitstellung von zwei zweiten Druckfeldern, die im wesentlichen der Längsnut 54 gegenüberliegen, erhält man ohne großen Aufwand eine sehr gute Kräftekompensation, eine verbesserte Schmierung und damiteine wesentliche Erhöhung der Standzeit und der Belastung des Spritzverstell-Kolbens 10.FIG. 5 also shows a third exemplary embodiment for relieving the injection adjustment piston 10 of harmful radial forces. This embodiment is also based on the provision of a second pressure field, which is opposite to the first pressure field, but in this case it is divided into two second pressure fields in order to record as much as possible all the moments that occur on the injection adjustment piston 10. Here, too, the spray adjustment piston with control slide is constructed in the same way as in the exemplary embodiment according to FIGS. 1 and 3, so that a supplementary description in this regard is not necessary. In a departure from the exemplary embodiment according to FIG. 1, a first connecting channel 69 and a second connecting channel 70 are now provided between the cylinder sleeve 61 and the adjacent housing 6 of the fuel injection pump, which, starting from the pressure medium inlet 55, initially run parallel to a surface line of the cylinder sleeve 61 and then in each case a half-ring groove 72 or 73 pass over, which lead to a location on the circumference of the cylinder sleeve 61 which lies diametrically to the entry of the pressure medium inlet 55 into the cylinder 11. There, the cylinder sleeve has a first opening 75 and a second opening 74, via which the connecting channels 69 and 70 have a connection to the interior of the cylinder 11 in the region between the cylinder 11 and the outer surface of the injection-adjusting piston. In this area, second pressure fields build up, which are symbolized as F da in the drawing. These forces are symmetrical to the center line of the pin 7 so that they ensure a uniform force balance on the injection-adjusting piston 10. They counteract the resulting contact forces FA and FB, which result from the loading of the first pressure field in the area of the pressure medium inlet 55. They also counteract at least one force component of the tilting forces exerted by the tilting moment on the actuating piston. With the provision of two second pressure fields, which essentially lie opposite the longitudinal groove 54, very good force compensation, improved lubrication and, consequently, a substantial increase in the service life and the load on the injection-adjusting piston 10 are obtained without great effort.

Figur 6 zeigt eine Alternative der Kanalführung der Verbindungskanäle, die hier als erster Verbindungskanal 69' und zweiter Verbindungskanal 70' wendelförmig verlaufen, ausgehend von dem Druckmittelzulauf 55. Vorteilhaft ist dabei die Ausarbeitung der Verbindungskanäle als Rillen, die anschließend durch die eingepreßte Zylinderhülse verschlossen werden, bis auf den Zulauf und die Durchtritte 75 und 74.FIG. 6 shows an alternative to the ducting of the Connection channels, which here are the first connection channel 69 ' and the second connecting channel 70 'run helically, starting from the pressure medium inlet 55. It is advantageous thereby the elaboration of the connecting channels as grooves that then through the pressed-in cylinder sleeve be closed, except for the inlet and the passages 75 and 74.

Claims (17)

  1. Fuel injection pump with an injection-adjusting piston (10) which adjusts the start of the injection and which is connected via a coupling part (7) to an adjustable part (3) of a cam drive, composed of a cam carrier part and at least one piston drive following the cam of the cam carrier part, of the fuel injection pump and which bounds a working space (14) in a cylinder (11), which working space (14) is acted on by a controllable medium by means of which the injection-adjusting piston (10) can be set counter to a restoring force (16) and with a control slide (24) which is arranged in the injection-adjusting piston (10) in a cylinder hole (22) which is coaxial to the axis of the injection-adjusting piston (10), and which can be displaced in the axial direction of the injection-adjusting piston (10) and can be adjusted counter to the force of a control spring (30) by a control pressure and controls in the cylinder hole (22) with control edges (40, 46) the connection between the working space (14) and an inflow (48, 50, 53, 55) of pressure medium from a pressure medium source, or an outflow (41) of pressure medium to a release space, the cylinder (11) being connected in its central region, at the point where the coupling part (7) passes through from the cam drive to the injection-adjusting piston, to a pump interior (4) in which the cam drive is arranged, the injection-adjusting piston (10) having on one side of its envelope surface a depression (9) in which the coupling part (7) engages, characterized in that at least one recess (54) which extends essentially in the axial direction of the injection-adjusting piston is provided between the envelope surface of the injection-adjusting piston (10) and the wall of the cylinder (11) in the region of a radial plane, passing through the coupling part (7), of the injection-adjusting piston, to which recess (54) a line (55) which starts from the pressure medium source and opens into the cylinder is continuously connected, and a first pressure field (66) is generated between the envelope surface of the injection-adjusting piston (10) and the wall of the cylinder (11) and at least a second pressure field is generated at a point (57, 67, 75, 74) on the cylinder lying essentially diametrically opposite the recess, which second pressure field counteracts the first pressure field (66) and tilting forces on the injection-adjusting piston which originate from forces resulting from the cam drive.
  2. Fuel injection pump according to Claim 1, characterized in that the at least one second pressure field is generated by a compression spring clamped between depression and coupling part.
  3. Fuel injection pump according to Claim 1, characterized in that the at least one second pressure field is generated by virtue of the fact that the point (57, 67, 75, 74) is connected to the recess (54) via a connecting duct.
  4. Fuel injection pump according to Claim 3, characterized in that the coupling part (7) encloses, in the depression (9), a pressure space (57) which is continuously connected to the recess (54) as a point lying essentially opposite the recess (54) and in which the at least one second pressure field is generated (Figure 1).
  5. Fuel injection pump according to Claim 4, characterized in that the recess (54) and the pressure space (57) are each continuously connected by means of a pressure duct (53, 58) to an annular groove (51) provided on the control slide (24) (Figure 1).
  6. Fuel injection pump according to Claim 3, characterized in that an additional recess (67) is provided between the envelope surface of the injection-adjusting piston (10) and the wall of the cylinder, the second pressure field being formed in the region of said additional recess (67) as a point lying essentially opposite the recess (54) (Figure 2).
  7. Fuel injection pump according to Claim 6, characterized in that the recess (54) and the additional recess (67) are each continuously connected by means of a pressure duct (53, 68) to an annular groove (51) provided on the control slide (24).
  8. Fuel injection pump according to Claim 3 to 7, characterized in that the recess is embodied as a longitudinal groove (54).
  9. Fuel injection pump according to Claim 6, characterized in that the additional recess is embodied as a longitudinal groove (67).
  10. Fuel injection pump according to Claim 8 to 9, characterized in that the recess and the additional recess each respectively have a channel (71, 72) provided parallel to them, which channels (71, 72) project beyond the recesses (54, 67) in the longitudinal directions and open with their one end in to a release space (15).
  11. Fuel injection pump according to Claim 3, characterized in that two connecting ducts (69, 70) lead from the recess (54) to, in each case, one outlet (73, 74) in the region between the envelope surface of the injection-adjusting piston (10) and the wall of the cylinder (11), are arranged on each side of the coupling part (7) and, as a point lying essentially opposite the recess, are located essentially in a common radial plane together with the recess (54) (Fig. 5).
  12. Fuel injection pump according to one of the preceding claims, characterized in that the injection-adjusting piston (10) is guided in a cylinder sheath (61) which is open in the region of the depression (9), made of wear-resistant material and is inserted into the housing (6) of the fuel injection pump which is composed of less wear-resistant material.
  13. Fuel injection pump according to Claim 11, characterized in that the injection-adjusting piston (10) is guided in a cylinder sheath (61) which is open in the region of the depression (9), made of wear-resistant material and inserted into the housing (6), composed of less wear-resistant material of the fuel injection pump, and the connecting ducts (69, 70, 71, 72) are embodied as channels which are closed by the cylinder sheath (61) and provided in the wall of the housing and at whose ends the cylinder sheath (61) has in each case a through-opening (75, 74), which through-openings (75, 74) form the outlet of the connecting ducts.
  14. Fuel injection pump according to Claim 11 or 13, characterized in that the connecting ducts (69, 70) extend from the recess (54) to its outlets (75, 74) in a helical shape.
  15. Fuel injection pump according to Claim 12 to 13, characterized in that the injection-adjusting piston (10) has an annular groove (63) into which a metallic sealing ring (64) is inserted which bears elastically against the inner envelope surface of the cylinder sheath (61).
  16. Fuel injection pump according to one of the preceding claims, characterized in that a first duct (48) and a second duct (56) are provided in the injection-adjusting piston (10), which ducts (48, 56) each connect the working space (14) to the cylinder hole (22), the junction of these ducts being controlled in each case by one of two control edges (40, 46) of the control slide (24), and the injection-adjusting piston (10) being activated by an actuation piston (33, 28) which is located outside the injection-adjusting piston and can be adjusted by the control pressure.
  17. Fuel injection pump according to one of the preceding claims, characterized in that the control slide (24) is activated by an actuating piston which is arranged outside the injection-adjusting piston (10) coaxially with respect thereto and counter to which the control spring acts, and the depression (9) in the injection-adjusting piston (10) is located in part of the longitudinal extent of the injection-adjusting piston (10), in which part the control slide (24) is also arranged.
EP97922883A 1996-07-25 1997-04-26 Fuel injection pump with an injection adjusting piston which adjusts the injection beginning Expired - Lifetime EP0852666B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19629947A DE19629947A1 (en) 1996-07-25 1996-07-25 Fuel injection pump with a spray adjustment piston which serves to adjust the start of injection
DE19629947 1996-07-25
PCT/DE1997/000862 WO1998004822A1 (en) 1996-07-25 1997-04-26 Fuel injection pump with an injection adjusting piston which adjusts the injection beginning

Publications (2)

Publication Number Publication Date
EP0852666A1 EP0852666A1 (en) 1998-07-15
EP0852666B1 true EP0852666B1 (en) 2002-03-13

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EP97922883A Expired - Lifetime EP0852666B1 (en) 1996-07-25 1997-04-26 Fuel injection pump with an injection adjusting piston which adjusts the injection beginning

Country Status (8)

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US (1) US6116220A (en)
EP (1) EP0852666B1 (en)
JP (1) JP2000500208A (en)
KR (1) KR19990063682A (en)
CN (1) CN1084833C (en)
DE (2) DE19629947A1 (en)
ES (1) ES2176738T3 (en)
WO (1) WO1998004822A1 (en)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19849925A1 (en) * 1998-10-29 2000-05-04 Bosch Gmbh Robert Fuel injection pump
US20030180712A1 (en) * 2002-03-20 2003-09-25 Biostratum Ab Inhibition of the beta3 subunit of L-type Ca2+ channels
DE10355027A1 (en) * 2003-11-25 2005-06-23 Robert Bosch Gmbh High-pressure pump, in particular for a fuel injection device of an internal combustion engine
CN101418759B (en) * 2008-11-17 2010-04-14 江阴林格科技有限公司 Stroke sensor for advance device of dispensing pump with low-voltage terminal fixed at one end
CN101806264B (en) * 2009-02-12 2011-10-19 南京威孚金宁有限公司 New electronic control dispensing pump
US8210156B2 (en) * 2009-07-01 2012-07-03 Ford Global Technologies, Llc Fuel system with electrically-controllable mechanical pressure regulator
US8495987B2 (en) * 2010-06-10 2013-07-30 Stanadyne Corporation Single piston pump with dual return springs
CN103244328B (en) * 2012-06-20 2016-06-08 南京威孚金宁有限公司 Pressure regulation timing advancer

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB925979A (en) * 1960-08-30 1963-05-15 Cav Ltd Liquid fuel injection pumps
US4037574A (en) * 1976-05-21 1977-07-26 Stanadyne, Inc. Timing control for fuel injection pump
US4594988A (en) * 1985-04-15 1986-06-17 Tompkins Jr Martin J Method for building or repairing rotary injection fuel pump piston cylinders
US4748958A (en) * 1986-11-12 1988-06-07 Ash Eugene G Method and means for repairing injection fuel pump pistons
US5263457A (en) * 1989-12-06 1993-11-23 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
JPH0814067A (en) * 1994-06-24 1996-01-16 Zexel Corp Servo valve type timer for fuel injection pump
GB9413994D0 (en) * 1994-07-12 1994-08-31 Lucas Ind Plc Advance piston mounting
GB9414308D0 (en) * 1994-07-15 1994-09-07 Lucas Ind Plc Advance mechanism
DE4440749A1 (en) * 1994-11-15 1996-05-23 Bosch Gmbh Robert Fuel injection pump

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CN1084833C (en) 2002-05-15
US6116220A (en) 2000-09-12
ES2176738T3 (en) 2002-12-01
DE19629947A1 (en) 1998-01-29
DE59706607D1 (en) 2002-04-18
CN1197498A (en) 1998-10-28
EP0852666A1 (en) 1998-07-15
WO1998004822A1 (en) 1998-02-05
JP2000500208A (en) 2000-01-11
KR19990063682A (en) 1999-07-26

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