EP0812384B1 - Fuel-injection pump for internal-combustion engines - Google Patents

Fuel-injection pump for internal-combustion engines Download PDF

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Publication number
EP0812384B1
EP0812384B1 EP96934435A EP96934435A EP0812384B1 EP 0812384 B1 EP0812384 B1 EP 0812384B1 EP 96934435 A EP96934435 A EP 96934435A EP 96934435 A EP96934435 A EP 96934435A EP 0812384 B1 EP0812384 B1 EP 0812384B1
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EP
European Patent Office
Prior art keywords
valve
pressure
pump
connection
controlled
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
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EP96934435A
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German (de)
French (fr)
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EP0812384A1 (en
Inventor
Christian Taudt
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • 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
    • 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
    • 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 relates to a fuel injection pump for Internal combustion engines according to the preamble of claim 1 out.
  • a fuel injection pump for Internal combustion engines according to the preamble of claim 1 out.
  • DE-A1-43 41 932 Known fuel injection pump is the reset space of the Pressure control valve from a certain temperature that the warm internal combustion engine corresponds to a controlled valve relieved. From this operating point the pressure control valve works as intended Type to adjust the pressure of the pump interior To control the start of spraying depending on the speed.
  • this known device is a special one Setting the start of spraying when the internal combustion engine is cold only controllable depending on temperature.
  • the fuel injection pump with the characterizing features of claim 1 has the advantage that independent of the control of the controlled valve, depending on the temperature, there is also the possibility of relieving the pressure in the interior of the pump to cause relief of the return space, which then the mode of operation of the pressure control valve is converted into the mode of operation which is provided for an internal combustion engine which is at operating temperature, regardless of the actual temperature of the internal combustion engine.
  • the influencing of the start of spraying controlled by the pressure control valve when the internal combustion engine is not at operating temperature is switched off or the particular mode of operation of this pressure control valve is limited as a function of the speed.
  • Claim 2 An advantageous development of the invention Claim 2 is the control of the controlled valve in connection with the control of the Pump interior pressure advantageous to improve such that now both a load-dependent, and temperature and speed-dependent influencing of the pressure in the Pump interior allows control of the start of spraying is.
  • the limiting valve is advantageous as Slider valve designed, which is a particularly exact Switching point setting enabled.
  • More beneficial Embodiments of the invention are in the further Subclaims 3 to 6 and have the advantage that Switching accuracy to control the pump interior pressure too improve. The can compared to the state of the Technology to be provided in addition easily integrate into existing solutions under Use of many existing series parts.
  • FIG. 1 shows a schematic representation of a distributor injection pump in Longitudinal section
  • Figure 2 shows the essential part of the invention
  • Figure 3 shows a modified embodiment of the Embodiment of Figure 2 and Figure 4, a third Execution of the invention with a separately provided Spool.
  • a pump piston 1 In the distributor fuel injection pump shown in Figure 1
  • a pump piston 1 In a known manner, a pump piston 1 is provided, which a cam disk 2 rotating from a drive shaft 3 the fuel injection pump is driven and with it Cam track 4 runs on rollers 5 of a roller ring 6, in a back and forth and at the same time rotating movement offset, by the rotation of the pump piston at the same time as Serves distributor.
  • the pump piston closes in one in the housing 7 of the fuel injection pump arranged cylinder 8 Cylinder bore a pump work space 9 on the front, in the suction stroke of the pump piston via suction grooves 10 and one Suction channel 11 fuel drawn from a pump interior 12 is and in its pressure stroke via a longitudinal channel 14 which of the end of the pump piston, and one with this Longitudinal channel 14 connected distributor groove 15 fuel to one is promoted by a plurality of pressure channels 16.
  • These pressure channels 16 are at regular intervals around the pump piston from the cylinder bore arranged outgoing and insert over each Pressure valve 17 to a not shown Fuel injector.
  • the amount of fuel supplied to this is determined by the axial position of a ring slide 18, the to a part of the projecting into the pump interior 12
  • Pump piston 1 is longitudinally displaceable. Through the front edge of the ring slide 18 becomes one with the longitudinal channel 14 connected cross bore 19 from a certain Pump piston delivery stroke opened so that the Pump work space in the pump interior is relieved and the High-pressure delivery phase with injection is ended.
  • the position of the ring slide is controlled by a speed controller 20 controlled, which has a control lever 21, on the one hand is coupled to the ring slide 18 and on the other hand by a control spring 22 is acted upon by a Regulator lever 23 can be preloaded more or less.
  • an adjusting sleeve 24 acts Centrifugal speed sensor 25, the centrifugal weights 26 about Gear transmission 27, 28 driven by the drive shaft 3 and the regulator sleeve 24 with increasing speed on a sleeve carrier 30 against the force of the control spring 22 push.
  • a spray adjuster 31 is also provided, which in the drawing is shown folded into the plane by 90 °.
  • This has one Spray adjuster piston 32 on the front of a work space 33 encloses in one cylinder bore and on its other End face is acted upon by a return spring 34.
  • the Injection adjuster piston is connected via a pin 36 to the Coupled roller ring 6, which is mounted in the pump housing and at its rotation the start of the stroke of the cam disc 4 and so that the pump piston 1 depending on the direction of rotation earlier or later with respect to the angular position of the drive shaft 3 or the rotational position of the pump piston 1.
  • the adjustment of the Injection adjuster piston 32 takes place in the working space 33 introduced pressure medium, which via a throttle connection 37 in Spray adjuster piston is supplied. Serves as a pressure source the pump interior 12, into which a feed pump 38 which is driven synchronously by the drive shaft 3, Fuel to supply the pump work space 9 is promoted.
  • a pressure control valve 39 controlled, which has a control piston 40 as a control element, which is arranged displaceably in a cylinder bore 51 one end face one with the pump interior connected pressure space 41 and limited to its other Front side of a spring providing a restoring force 42 is applied.
  • the control piston controls a discharge 43 from the front Pump interior 12 to a relief space, the present the suction side of the fuel pump 38 or the Fuel tank 44 can be.
  • the spring 42 receiving space is as a reset space 54 via a throttle 45 in the control piston connected to the pressure chamber 41 and via a Relief line 46 connected to a controlled valve 52. This is shown in more detail in FIGS. 2 to 4.
  • a distributor injection pump with a Lifting cam and a roller ring described by the Injection start adjuster 31 is adjusted to adjust the Start of spraying.
  • a spray start adjuster can also differently ordered cam drives of injection pumps be adjusted, e.g. B. in radial piston pumps a cam ring or facilities, e.g. B. for in-line pumps to adjust the relative cam position to the drive shaft.
  • cam-bearing part which is essentially is fixed
  • a roller-bearing part, which as Cam follower scans the cam track can be adjusted to the to achieve the desired spray start adjustment result.
  • the pressure in the pump interior can preferably be used as an adjustment medium or control pressure for the injection start adjuster which also with increasing speed via its adjusting piston and the cam gear adjusts the start of spraying.
  • Interior pressure depending on other parameters than affect the speed to certain pump functions in relation to the start of spray setting. This can in particular a load dependent factor can be introduced by a variable drain throttle 47 provided on the adjusting sleeve 24 becomes.
  • the adjusting sleeve has an opening in its wall, which in the course of the adjustment of the adjusting sleeve 24 increasingly in Coverage with a drain channel 48 comes within the Sleeve carrier 30 runs. This drainage channel leads over the controlled valve 52 to the relief chamber, the suction side of the Fuel feed pump 38 or the fuel reservoir 44 back.
  • FIG 2 is the pressure control valve 39 which is in connection with the controlled valve 52, a first pressure control device 49 forms, shown in more detail. It is again as above described, representing a second pressure control device 50 Device for additional influencing of the Pump interior pressure consisting of the discharge throttle 47 and the adjusting sleeve 24, through the load-dependent fuel quantities are branched off from the pump interior, reproduced.
  • the controlled valve 52 is in the relief line 46 of the Reset room 54 arranged. It consists of one Ball check valve with a ball 56 as a closing member, the by a spring 57 with a defined preload in Closing direction is kept.
  • the controlled valve 52 is the temperature of the Controlled internal combustion engine characteristic size.
  • FIG temperature-dependent expansion element 59 the for example the cooling water temperature of the internal combustion engines may be exposed or may be electrically heated in Depending on the temperature or a substitute parameter.
  • a slide valve member 61 which acts as a piston a bore 62 coaxial with the controlled valve 52 is arranged displaceably, and by a return spring 63 is loaded towards the expansion element 59.
  • the Slider valve member continues in an adjusting mandrel 64 which axially in a discharge line 46 with the controlled Valve 52 on the one hand and the bore 62 on the other connecting channel protrudes so that with a shift of the slide valve member 61 through the expansion element 59 of the Setting mandrel 64 comes into contact with the ball 56 and this of lifts off its seat and thus opens the control valve. So that will the connection of the relief line 46 to the relief space manufactured.
  • the slide valve member controls the continued drain channel 48 of the second Pressure control device 50.
  • This channel opens into the Hole 62 that he in the cold engine in Figure 2 shown position of the slide valve member 61 by this is closed and when the internal combustion engine is warm which the slide valve member together with the setting mandrel is shifted to open the controlled valve 52, opened is.
  • the channel 48 leads in from the bore 62 electromagnetically operated switching valve 66 for Relief chamber 44. The switching valve, the open or Closed position is then significant when the slide valve member 61 has opened the drain channel 48 is in Dependency on operating parameters other than temperature controlled the internal combustion engine. It then closes if, as mentioned at the beginning, e.g. B.
  • a limit valve 106 is provided, consisting of a Slider 107, which is tight in a cylinder bore is movable and with its front side a work space 109 includes that via a throttle 108 in constant Connection to the pump interior 12 is.
  • the work room 109 opposite one acts on the slide 107 Actuating force in the form of a compression spring 110, which in particular is adjustable.
  • a channel 111 is provided in the slide, the against the corresponding deflection of the slide 107 the force of spring 110 in conjunction with one Connection channel 112 arrives from the relief line 46 branches and thus in constant connection with the Reset room 54 is.
  • channel 111 opens into the space accommodating the spring 110, which in turn has a Line 114 with the relief chamber 44 and the Fuel tank is connected.
  • This valve 106 is part of the first pressure control device 49. With it achieved that from a certain internal pressure in Pump interior 12 a relief connection between the Reset space 54 and the relief space 44 produced becomes. This happens regularly when you reach one certain speed at which a special early adjustment the start of spraying or a special setting of the Start of injection and the fact that the internal combustion engine is not yet warm, is not necessary. With With the help of this limit valve 106, the use of first pressure control device 49 to a specific one Speed resulting from the interior pressure of the pump interior 12 derivable is limited.
  • the load-dependent is basically Influencing the interior pressure allows when the required operating temperature is reached and that Ball check valve 156 constantly through the expansion element 59 is lifted off.
  • FIG. 4 Another embodiment of such an influence shows the embodiment of Figure 4.
  • Pressure control device 49 is shown in Figure 2.
  • Figure 4 is a piston valve 100 provided in a Cylinder bore 101 is slidably arranged and on one side is acted upon by a return spring 103 is closed while its other end face Cylinder bore 101 includes a working space 102 that constantly with the relief line 46 or the reset room 54 is connected. Because of the pressure in this recovery room the spool can move against the force of the return spring 103 to be moved up to a stop 104 such that the leading through the cylinder bore 101 Connection line to the continuing line through the Piston slide is closed.

Description

Stand der TechnikState of the art

Die Erfindung geht von einer Kraftstoffeinspritzpumpe für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1 aus. Bei einer derartigen, durch die DE-A1-43 41 932 bekannte Kraftstoffeinspritzpumpe ist der Rückstellraum des Drucksteuerventils ab einer bestimmten Temperatur, die der betriebswarmen Brennkraftmaschine entspricht über ein gesteuertes Ventil entlastet. Ab diesem Betriebspunkt arbeitet das Drucksteuerventil in seiner bestimmungsgemäßen Art, den Druck des Pumpeninnenraums zur Einstellung des Spritzbeginns in Abhängigkeit von der Drehzahl zu steuern. Mit dieser bekannten Einrichtung ist eine besondere Einstellung des Spritzbeginns bei kalter Brennkraftmaschine ausschließlich temperaturabhängig steuerbar.The invention relates to a fuel injection pump for Internal combustion engines according to the preamble of claim 1 out. In such a, by DE-A1-43 41 932 Known fuel injection pump is the reset space of the Pressure control valve from a certain temperature that the warm internal combustion engine corresponds to a controlled valve relieved. From this operating point the pressure control valve works as intended Type to adjust the pressure of the pump interior To control the start of spraying depending on the speed. With this known device is a special one Setting the start of spraying when the internal combustion engine is cold only controllable depending on temperature.

Vorteile der ErfindungAdvantages of the invention

Die Kraftstoffeinspritzpumpe mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat dem gegenüber den Vorteil, daß unabhängig von der Steuerung des gesteuerten Ventils in Abhängigkeit von der Temperatur zusätzlich die Möglichkeit geschaffen ist, in Abhängigkeit vom sich einstellenden Druck im Pumpeninnenraum eine Entlastung des Rückstellraumes zu bewirken, was dann die Arbeitsweise des Drucksteuerventils in die Arbeitsweise überführt, die für eine betriebswarme Brennkraftmaschine vorgesehen ist, unabhängig von der tatsächlich vorliegenden Temperatur der Brennkraftmaschine. Somit wird bei zunehmender Drehzahl, die über das Drucksteuerventil gesteuerte Beeinflussung des Spritzbeginns bei nicht betriebswarmer Brennkraftmaschine ausgeschaltet bzw. die besondere Betriebsweise dieses Drucksteuerventils drehzahlabhängig begrenzt. Bei hohen Drehzahlen ist die besondere Spritzbeginnverstellung (KSB = Kaltstartbeschleunigung) nicht mehr erforderlich.The fuel injection pump with the characterizing features of claim 1 has the advantage that independent of the control of the controlled valve, depending on the temperature, there is also the possibility of relieving the pressure in the interior of the pump to cause relief of the return space, which then the mode of operation of the pressure control valve is converted into the mode of operation which is provided for an internal combustion engine which is at operating temperature, regardless of the actual temperature of the internal combustion engine. Thus, with increasing speed, the influencing of the start of spraying controlled by the pressure control valve when the internal combustion engine is not at operating temperature is switched off or the particular mode of operation of this pressure control valve is limited as a function of the speed. At high speeds, the special injection onset adjustment (KSB = K s old tart b eschleunigung) is no longer required.

Eine vorteilhafte Weiterbildung der Erfindung nach Patentanspruch 2 besteht darin, die Steuerung des gesteuerten Ventils in Verbindung mit der Steuerung des Pumpeninnenraumdrucks vorteilhaft zu verbessern derart, daß nun sowohl eine lastabhängige, als auch temperatur- und drehzahlabhängige Beeinflussung des Drucks im Pumpeninnenraum zur Steuerung des Spritzbeginns ermöglicht ist. Das Begrenzungsventil ist dabei vorteilhaft als Schieberventil ausgebildet, was eine besonders exakte Schaltpunkteinstellung ermöglicht. Weitere vorteilhafte Ausgestaltungen der Erfindung sind in den weiteren Unteransprüchen 3 bis 6 gegeben und haben den Vorteil, die Schaltgenauigkeit zur Steuerung des Pumpeninnenraumdrucks zu verbessern. Dabei lassen sich die gegenüber dem Stand der Technik zusätzlich zu erbringenden Ausgestaltungen in einfacher Weise in bestehende Lösungen integrieren unter Verwendung vieler vorhandener Serienteile.An advantageous development of the invention Claim 2 is the control of the controlled valve in connection with the control of the Pump interior pressure advantageous to improve such that now both a load-dependent, and temperature and speed-dependent influencing of the pressure in the Pump interior allows control of the start of spraying is. The limiting valve is advantageous as Slider valve designed, which is a particularly exact Switching point setting enabled. More beneficial Embodiments of the invention are in the further Subclaims 3 to 6 and have the advantage that Switching accuracy to control the pump interior pressure too improve. The can compared to the state of the Technology to be provided in addition easily integrate into existing solutions under Use of many existing series parts.

Zeichnungdrawing

Drei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und werden in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine schematische Darstellung einer Verteilereinspritzpumpe im Längsschnitt, Figur 2 den erfindungswesentlichen Teil der Verteilerkraftstoffeinspritzpumpe gemäß Figur 1 mit Regelmuffe, Spritzversteller, Druckregelventil und Drucksteuereinrichtung für ein erstes Ausführungsbeispiel, Figur 3 eine abgewandelte Ausführungsform des Ausführungsbeispiels nach Figur 2 und Figur 4 eine dritte Ausführung der Erfindung mit einem separat vorgesehenem Kolbenschieber.Three embodiments of the invention are in the Drawing and are shown in the following Description explained in more detail. 1 shows a schematic representation of a distributor injection pump in Longitudinal section, Figure 2 shows the essential part of the invention Distributor fuel injection pump according to Figure 1 with Control sleeve, spray adjuster, pressure control valve and Pressure control device for a first embodiment Figure 3 shows a modified embodiment of the Embodiment of Figure 2 and Figure 4, a third Execution of the invention with a separately provided Spool.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Bei der in Figur 1 gezeigten Verteilerkraftstoffeinspritzpumpe ist in bekannter Weise ein Pumpenkolben 1 vorgesehen, der über eine Nockenscheibe 2, die rotierend von einer Antriebswelle 3 der Kraftstoffeinspritzpumpe angetrieben wird und mit ihrer Nockenbahn 4 auf Rollen 5 eines Rollenrings 6 abläuft, in eine hin- und hergehende und zugleich rotierende Bewegung versetzt, wobei durch die Rotation der Pumpenkolben zugleich als Verteiler dient. Der Pumpenkolben schließt in einem im Gehäuse 7 der Kraftstoffeinspritzpumpe angeordneten Zylinder 8 mit Zylinderbohrung stirnseitig einen Pumpenarbeitsraum 9 ein, in den beim Saughub des Pumpenkolbens über Saugnuten 10 und einen Saugkanal 11 Kraftstoff aus einem Pumpeninnenraum 12 angesaugt wird und bei seinem Druckhub über einen Längskanal 14, der von der Stirnseite des Pumpenkolbens ausgeht, und eine mit diesem Längskanal 14 verbundenen Verteilernut 15 Kraftstoff zu einem von mehreren Druckkanälen 16 gefördert wird. Diese Druckkanäle 16 sind in regelmäßigem Abstand um den Pumpenkolben herum von der Zylinderbohrung abgehend angeordnet und führen über je ein Druckventil 17 zu einer nicht weiter dargestellten Kraftstoffeinspritzdüse. Die dieser zugeführte Kraftstoffmenge wird bestimmt durch die axiale Lage eines Ringschiebers 18, der auf einen in den Pumpeninnenraum 12 ragenden Teil des Pumpenkolbens 1 längs verschiebbar ist. Durch die Stirnkante des Ringschiebers 18 wird dabei eine mit dem Längskanal 14 verbundene Querbohrung 19 ab einem bestimmten Pumpenkolbenförderhub aufgesteuert, so daß der Pumpenarbeitsraum in den Pumpeninnenraum entlastet wird und die Hochdruckförderphase mit Einspritzung beendet wird. Die Stellung des Ringschiebers wird durch einen Drehzahlregler 20 gesteuert, der einen Reglerhebel 21 aufweist, der einerseits mit dem Ringschieber 18 gekoppelt ist und andererseits von einer Regelfeder 22 beaufschlagt ist, die durch einen Reglerhebel 23 mehr oder weniger stark vorspannbar ist. Entgegen der Regelfeder wirkt eine Verstellmuffe 24 eines Fliehkraftdrehzahlgebers 25, dessen Fliehgewichte 26 über ein Zahnradgetriebe 27, 28 von der Antriebswelle 3 angetrieben werden und dabei die Reglermuffe 24 mit zunehmender Drehzahl auf einen Muffenträqer 30 entgegen der Kraft der Regelfeder 22 schieben.In the distributor fuel injection pump shown in Figure 1 In a known manner, a pump piston 1 is provided, which a cam disk 2 rotating from a drive shaft 3 the fuel injection pump is driven and with it Cam track 4 runs on rollers 5 of a roller ring 6, in a back and forth and at the same time rotating movement offset, by the rotation of the pump piston at the same time as Serves distributor. The pump piston closes in one in the housing 7 of the fuel injection pump arranged cylinder 8 Cylinder bore a pump work space 9 on the front, in the suction stroke of the pump piston via suction grooves 10 and one Suction channel 11 fuel drawn from a pump interior 12 is and in its pressure stroke via a longitudinal channel 14 which of the end of the pump piston, and one with this Longitudinal channel 14 connected distributor groove 15 fuel to one is promoted by a plurality of pressure channels 16. These pressure channels 16 are at regular intervals around the pump piston from the cylinder bore arranged outgoing and insert over each Pressure valve 17 to a not shown Fuel injector. The amount of fuel supplied to this is determined by the axial position of a ring slide 18, the to a part of the projecting into the pump interior 12 Pump piston 1 is longitudinally displaceable. Through the front edge of the ring slide 18 becomes one with the longitudinal channel 14 connected cross bore 19 from a certain Pump piston delivery stroke opened so that the Pump work space in the pump interior is relieved and the High-pressure delivery phase with injection is ended. The The position of the ring slide is controlled by a speed controller 20 controlled, which has a control lever 21, on the one hand is coupled to the ring slide 18 and on the other hand by a control spring 22 is acted upon by a Regulator lever 23 can be preloaded more or less. Contrary to the rule spring, an adjusting sleeve 24 acts Centrifugal speed sensor 25, the centrifugal weights 26 about Gear transmission 27, 28 driven by the drive shaft 3 and the regulator sleeve 24 with increasing speed on a sleeve carrier 30 against the force of the control spring 22 push.

Zur Steuerung des Spritzbeginns der Kraftstoffeinspritzpumpe ist ferner ein Spritzversteller 31 vorgesehen, der in der Zeichnung um 90° in die Ebene geklappt dargestellt ist. Dieser weist einen Spritzverstellerkolben 32 auf, der stirnseitig einen Arbeitsraum 33 in einer Zylinderbohrung einschließt und auf seiner anderen Stirnseite von einer Rückstellfeder 34 beaufschlagt ist. Der Spritzverstellerkolben ist über einen Bolzen 36 mit dem Rollenring 6 gekoppelt, der im Pumpengehäuse gelagert ist und bei seiner Verdrehung den Hubbeginn der Nockenscheibe 4 und damit des Pumpenkolbens 1 je nach Drehrichtung früher oder später in bezug auf die Winkelstellung der Antriebswelle 3 bzw. der Drehlage des Pumpenkolbens 1 legt. Die Verstellung des Spritzverstellerkolbens 32 erfolgt über in den Arbeitsraum 33 eingebrachtes Druckmittel, das über eine Drosselverbindung 37 im Spritzverstellerkolben zugeführt wird. Als Druckquelle dient dabei der Pumpeninnenraum 12, in den durch eine Förderpumpe 38, die drehzahlsynchron von der Antriebswelle 3 angetrieben wird, Kraftstoff zur Versorgung auch des Pumpenarbeitsraumes 9 gefördert wird. Zusätzlich zu dem in Abhängigkeit von der Drehzahl ansteigenden Förderdruck der Förderpumpe wird der Druck im Pumpeninnenraum 12 noch durch ein Drucksteuerventil 39 gesteuert, das einen Steuerkolben 40 als Steuerglied aufweist, das in einer Zylinderbohrung 51 verschiebbar angeordnet ist, auf seiner einen Stirnseite einen mit dem Pumpeninnenraum verbundenen Druckraum 41 begrenzt und auf seiner anderen Stirnseite von einer eine Rückstellkraft bereitstellende Feder 42 beaufschlagt wird. Mit seiner dem Druckraum 41 begrenzenden Stirnseite steuert der Steuerkolben einen Abfluß 43 vom Pumpeninnenraum 12 zu einem Entlastungsraum, der im vorliegenden die Saugseite der Kraftstofförderpumpe 38 oder der Kraftstoffvorratsbehälter 44 sein kann. Der die Feder 42 aufnehmende Raum ist als Rückstellraum 54 über eine Drossel 45 im Steuerkolben mit dem Druckraum 41 verbunden und über eine Entlastungsleitung 46 mit einem gesteuerten Ventil 52 verbunden. Diese ist in den Figuren 2 bis 4 näher dargestellt.To control the start of injection of the fuel injection pump a spray adjuster 31 is also provided, which in the drawing is shown folded into the plane by 90 °. This has one Spray adjuster piston 32 on the front of a work space 33 encloses in one cylinder bore and on its other End face is acted upon by a return spring 34. The Injection adjuster piston is connected via a pin 36 to the Coupled roller ring 6, which is mounted in the pump housing and at its rotation the start of the stroke of the cam disc 4 and so that the pump piston 1 depending on the direction of rotation earlier or later with respect to the angular position of the drive shaft 3 or the rotational position of the pump piston 1. The adjustment of the Injection adjuster piston 32 takes place in the working space 33 introduced pressure medium, which via a throttle connection 37 in Spray adjuster piston is supplied. Serves as a pressure source the pump interior 12, into which a feed pump 38 which is driven synchronously by the drive shaft 3, Fuel to supply the pump work space 9 is promoted. In addition to that depending on the Speed increasing feed pressure of the feed pump becomes the pressure in the pump interior 12 by a pressure control valve 39 controlled, which has a control piston 40 as a control element, which is arranged displaceably in a cylinder bore 51 one end face one with the pump interior connected pressure space 41 and limited to its other Front side of a spring providing a restoring force 42 is applied. With its delimiting the pressure chamber 41 The control piston controls a discharge 43 from the front Pump interior 12 to a relief space, the present the suction side of the fuel pump 38 or the Fuel tank 44 can be. The spring 42 receiving space is as a reset space 54 via a throttle 45 in the control piston connected to the pressure chamber 41 and via a Relief line 46 connected to a controlled valve 52. This is shown in more detail in FIGS. 2 to 4.

Im vorstehenden wurde eine Verteilereinspritzpumpe mit einer Hubnockenscheibe und einem Rollenring beschrieben, der von dem Spritzbeginnversteller 31 verstellt wird zur Einstellung des Spritzbeginns. Mit einem solchen Spritzbeginnversteller können auch anders geordnete Nockenantriebe von Einspritzpumpen verstellt werden, z. B. bei Radialkolbenpumpen ein Nockenring oder Einrichtungen, z. B. bei Reihenpumpen zur Verstellung der relativen Nockenlage zur Antriebswelle. Grundsätzlich kann entweder ein nockentragender Teil, der im wesentlichen feststehend ist, oder ein rollentragender Teil, der als Nockenfolger die Nockenbahn abtastet, verstellt werden, um das gewünschte Spritzbeginnverstellergebnis zu erzielen.In the above, a distributor injection pump with a Lifting cam and a roller ring described by the Injection start adjuster 31 is adjusted to adjust the Start of spraying. With such a spray start adjuster can also differently ordered cam drives of injection pumps be adjusted, e.g. B. in radial piston pumps a cam ring or facilities, e.g. B. for in-line pumps to adjust the relative cam position to the drive shaft. Basically can either a cam-bearing part, which is essentially is fixed, or a roller-bearing part, which as Cam follower scans the cam track, can be adjusted to the to achieve the desired spray start adjustment result.

Da sich der Druck im Pumpeninnenraum mit Hilfe des Drucksteuerventils steuern läßt, insbesondere so, daß er mit zunehmender Drehzah ansteigt, kann der Druck im Pumpeninnenraum vorzugsweise als Verstellmedium bzw. Steuerdruck für den Spritzbeginnversteller dienen der ebenso mit zunehmender Drehzahl über seinen Verstellkolben und das Nockengetriebe den Spritzbeginn verstellt. Es ist bekannt, den Innenraumdruck noch zusätzlich in Abhängigkeit von anderen Parametern als der Drehzahl zu beeinflussen, um bestimmte Pumpenfunktionen in bezug auf die Spritzbeginneinstellung zu erzielen. Dazu kann insbesondere ein lastabhängiger Faktor eingebracht werden, indem eine veränderliche Abflußdrossel 47 an der Verstellmuffe 24 vorgesehen wird. Dabei weist die Verstellmuffe in ihrer Wand eine Öffnung auf, die im Laufe der Verstellung der Verstellmuffe 24 zunehmend in Überdeckung mit einem Abflußkanal 48 kommt, der innerhalb des Muffenträgers 30 verläuft. Dieser Abflußkanal führt über das gesteuerte Ventil 52 zum Entlastungsraum, der Ansaugseite der Kraftstofförderpumpe 38 bzw. dem Kraftstoffvorratsbehälter 44 zurück.As the pressure in the pump interior changes with the help of the pressure control valve can control, especially so that it increases with speed increases, the pressure in the pump interior can preferably be used as an adjustment medium or control pressure for the injection start adjuster which also with increasing speed via its adjusting piston and the cam gear adjusts the start of spraying. It is known that Interior pressure depending on other parameters than affect the speed to certain pump functions in relation to the start of spray setting. This can in particular a load dependent factor can be introduced by a variable drain throttle 47 provided on the adjusting sleeve 24 becomes. The adjusting sleeve has an opening in its wall, which in the course of the adjustment of the adjusting sleeve 24 increasingly in Coverage with a drain channel 48 comes within the Sleeve carrier 30 runs. This drainage channel leads over the controlled valve 52 to the relief chamber, the suction side of the Fuel feed pump 38 or the fuel reservoir 44 back.

In Figur 2 ist das Drucksteuerventil 39, das in Verbindung mit dem gesteuerten Ventils 52 eine erste Drucksteuereinrichtung 49 bildet, näher dargestellt. Es ist nochmals, wie oben beschrieben, eine zweite Drucksteuereinrichtung 50 darstellende Einrichtung zur zusätzlichen Beeinflussung des Pumpeninnenraumdruckes bestehend aus der Abflußdrossel 47 und der Verstellmuffe 24, durch die lastabhängig Kraftstoffmengen aus dem Pumpeninnenraum abgezweigt werden, wiedergegeben. Das gesteuerte Ventil 52 ist dabei in der Entlastungsleitung 46 des Rückstellraumes 54 angeordnet. Es besteht hierbei aus einem Kugelrückschlagventil mit einer Kugel 56 als Schließglied, das von einer Feder 57 mit definierter Vorspannung in Schließrichtung gehalten wird. Das gesteuerte Ventil 52 wird dabei in Abhängigkeit von einer die Temperatur der Brennkraftmaschine kennzeichnenden Größe gesteuert. Dies geschieht in der beispielhaften Ausführung von Figur 2 über ein temperaturabhängig arbeitendes Dehnstoffelement 59, das beispielsweise der Kühlwassertemperatur der Brennkraftmaschinen ausgesetzt sein kann oder auch elektrisch beheizt sein kann in Abhängigkeit von der Temperatur oder einem Ersatzparameter. Dieses bewegt ein Schieberventilglied 61, das als Kolben in einer zum gesteuerten Ventil 52 koaxialen Bohrung 62 verschiebbar angeordnet ist, und von einer Rückstellfeder 63 zum Dehnstoffelement 59 hin belastet ist. Das Schieberventilglied setzt sich in einem Stelldorn 64 fort, der axial in einer die Entlastungsleitung 46 mit dem gesteuerten Ventil 52 einerseits und der Bohrung 62 andererseits verbindenden Kanal so hineinragt, daß bei einer Verschiebung des Schieberventilglieds 61 durch das Dehnstoffelement 59 der Stelldorn 64 in Kontakt mit der Kugel 56 kommt und diese von ihrem Sitz abhebt und somit das Steuerventil öffnet. Damit wird die Verbindung der Entlastungsleitung 46 zum Entlastungsraum hergestellt.In Figure 2 is the pressure control valve 39 which is in connection with the controlled valve 52, a first pressure control device 49 forms, shown in more detail. It is again as above described, representing a second pressure control device 50 Device for additional influencing of the Pump interior pressure consisting of the discharge throttle 47 and the adjusting sleeve 24, through the load-dependent fuel quantities are branched off from the pump interior, reproduced. The controlled valve 52 is in the relief line 46 of the Reset room 54 arranged. It consists of one Ball check valve with a ball 56 as a closing member, the by a spring 57 with a defined preload in Closing direction is kept. The controlled valve 52 is the temperature of the Controlled internal combustion engine characteristic size. this happens in the exemplary embodiment of FIG temperature-dependent expansion element 59, the for example the cooling water temperature of the internal combustion engines may be exposed or may be electrically heated in Depending on the temperature or a substitute parameter. This moves a slide valve member 61, which acts as a piston a bore 62 coaxial with the controlled valve 52 is arranged displaceably, and by a return spring 63 is loaded towards the expansion element 59. The Slider valve member continues in an adjusting mandrel 64 which axially in a discharge line 46 with the controlled Valve 52 on the one hand and the bore 62 on the other connecting channel protrudes so that with a shift of the slide valve member 61 through the expansion element 59 of the Setting mandrel 64 comes into contact with the ball 56 and this of lifts off its seat and thus opens the control valve. So that will the connection of the relief line 46 to the relief space manufactured.

Das Schieberventilglied steuert dabei zugleich den weitergeführten Abflußkanal 48 der zweiten Drucksteuereinrichtung 50. Dieser Kanal mündet so in die Bohrung 62 ein, daß er bei kalter Brennkraftmaschine in der in Figur 2 gezeigten Stellung des Schieberventilglieds 61 durch dieses verschlossen ist und bei warmer Brennkraftmaschine, bei dem das Schieberventilglied zusammen mit dem Stelldorn verschoben ist, um das gesteuerte Ventil 52 zu öffnen, geöffnet ist. Der Kanal 48 führt von der Bohrung 62 über ein elektromagnetisch betätigtes Schaltventil 66 zum Entlastungsraum 44. Das Schaltventil, dessen Offen- bzw. Schließstellung dann erheblich ist, wenn das Schieberventilglied 61 den Abflußkanal 48 geöffnet hat, wird in Abhängigkeit von anderen Betriebsparametern als der Temperatur der Brennkraftmaschine gesteuert. Es wird dann geschlossen, wenn, wie eingangs erwähnt, z. B. bei Betrieb des zugehörigen Kraftfahrzeugs mit Brennkraftmaschine in großer Höhe eine lastabhängige Verschiebung des Spritzbeginns im Teillastgebiet zu fehlerhafter Funktionsweise führen würde. Mit Hilfe des Schaltventils kann somit die lastabhängige Beeinflussung des Spritzbeginns immer dann bei warmer Brennkraftmaschine beeinflußt werden, wenn es entsprechende Betriebsparameter erfordern. Bei kalter Brennkraftmaschine dagegen ist gemäß der Darstellung in Figur 2 die lastabhängige Beeinflussung des Steuerdrucks im Pumpeninnenraum und damit des Spritzbeginns durch die zweite Drucksteuereinrichtung 50 zusätzlich abgeschaltet.The slide valve member controls the continued drain channel 48 of the second Pressure control device 50. This channel opens into the Hole 62 that he in the cold engine in Figure 2 shown position of the slide valve member 61 by this is closed and when the internal combustion engine is warm which the slide valve member together with the setting mandrel is shifted to open the controlled valve 52, opened is. The channel 48 leads in from the bore 62 electromagnetically operated switching valve 66 for Relief chamber 44. The switching valve, the open or Closed position is then significant when the slide valve member 61 has opened the drain channel 48 is in Dependency on operating parameters other than temperature controlled the internal combustion engine. It then closes if, as mentioned at the beginning, e.g. B. when operating the associated Motor vehicle with an internal combustion engine at high altitude load-dependent shift of the start of spraying in the partial load area would lead to incorrect functioning. With the help of Switching valve can thus influence the load-dependent Always start spraying when the internal combustion engine is warm be affected if there are appropriate operating parameters require. In contrast, in the case of a cold internal combustion engine, according to Representation in Figure 2, the load-dependent influence of Control pressure in the pump interior and thus the start of spraying by the second pressure control device 50 additionally switched off.

Zur Begrenzung des Einflusses des geschlossenen Zustandes des gesteuerten Ventils 52 auf den Druck im Pumpeninnenraum 12 bzw. auf die Spritzbeginnverstellung ist nun zusätzlich ein Begrenzungsventil 106 vorgesehen, bestehend aus einem Schieber 107, der in einer Zylinderbohrung dicht verschiebbar ist und mit seiner Stirnseite einen Arbeitsraum 109 einschließt, der über eine Drossel 108 in ständiger Verbindung mit dem Pumpeninnenraum 12 ist. Dem Arbeitsraum 109 gegenüberliegend wirkt auf den Schieber 107 eine Stellkraft in Form einer Druckfeder 110, die insbesondere einstellbar ist. Im Schieber ist ein Kanal 111 vorgesehen, der bei entsprechender Auslenkung des Schiebers 107 gegen die Kraft der Feder 110 in Verbindung mit einem Verbindungskanal 112 gelangt, der von der Entlastungsleitung 46 abzweigt und somit in ständiger Verbindung mit dem Rückstellraum 54 ist. Der Kanal 111 mündet andererseits in den die Feder 110 aufnehmenden Raum, der wiederum über eine Leitung 114 mit dem Entlastungsraum 44 bzw. den Kraftstoffvorratsbehälter verbunden ist. Dieses Ventil 106 ist Teil der ersten Drucksteuereinrichtung 49. Mit ihm wird erreicht, daß ab einem bestimmten Innendruck im Pumpeninnenraum 12 eine entlastende Verbindung zwischen dem Rückstellraum 54 und dem Entlastungsraum 44 hergestellt wird. Dies geschieht regelmäßig beim Erreichen einer bestimmten Drehzahl, bei der ein besondere Frühverstellung des Spritzbeginns bzw. eine besondere Einstellung des Spritzbeginns und der Tatsache, daß die Brennkraftmaschine noch nicht betriebswarm ist, nicht erforderlich ist. Mit Hilfe dieses Begrenzungsventils 106 kann der Einsatz der ersten Drucksteuereinrichtung 49 auf eine bestimmte Drehzahl, die aus dem Innenraumdruck des Pumpeninnenraumes 12 ableitbar ist begrenzt werden.To limit the influence of the closed state of the controlled valve 52 to the pressure in the pump interior 12 or on the spray start adjustment is now additional a limit valve 106 is provided, consisting of a Slider 107, which is tight in a cylinder bore is movable and with its front side a work space 109 includes that via a throttle 108 in constant Connection to the pump interior 12 is. The work room 109 opposite one acts on the slide 107 Actuating force in the form of a compression spring 110, which in particular is adjustable. A channel 111 is provided in the slide, the against the corresponding deflection of the slide 107 the force of spring 110 in conjunction with one Connection channel 112 arrives from the relief line 46 branches and thus in constant connection with the Reset room 54 is. On the other hand, channel 111 opens into the space accommodating the spring 110, which in turn has a Line 114 with the relief chamber 44 and the Fuel tank is connected. This valve 106 is part of the first pressure control device 49. With it achieved that from a certain internal pressure in Pump interior 12 a relief connection between the Reset space 54 and the relief space 44 produced becomes. This happens regularly when you reach one certain speed at which a special early adjustment the start of spraying or a special setting of the Start of injection and the fact that the internal combustion engine is not yet warm, is not necessary. With With the help of this limit valve 106, the use of first pressure control device 49 to a specific one Speed resulting from the interior pressure of the pump interior 12 derivable is limited.

Bei der Ausgestaltung nach Figur 2 wurde die Abschaltung der lastabhängigen Beeinflussung des Pumpeninnenraumdruckes über die gesteuerte Abflußdrossel 47 in der Verstellmuffe 24 mit Hilfe des Schieberventilglieds 61 erreicht, mit dem der Stelldorn 64 zur Betätigung des Ventilglieds 56 verbunden war. Bei dieser Ausgestaltung wird die Verbindung der Leitung 48 zum Entlastungsraum 44 ganz in die Abhängigkeit von der Temperatur gesteuert. Weitere Ausgestaltung gemäß Figur 3 ist nun die Steuerung dieser Abschaltung durch Sperren des Kanals 48 in die Funktion des Kugelrückschlagventils 156, 161, 157 belegt. Das in Figur 2 als einfaches Rückschlagventil mit einem Ventilglied in Form einer Kugel 56 wird nun ersetzt durch eine Kombination dieser mit einem Schieberventilglied 161, das eine Umfangsnut aufweist. Über dieses Schieberventilglied wird die Kugel 156 durch die Schließkraft, die Druckfeder 157, in Schließrichtung beaufschlagt. In dieser Stellung hat das Schieberventilglied 161, das in einer Zylinderbohrung gleitet, die durch diese Zylinderbohrung geführte Verbindung 48 zur weiterführenden Leitung 65, in der das Schaltventil 66 angeordnet ist, verschlossen. Öffnet nun das Kugelrückschlagventil entweder unter Einfluß des ansteigenden Druckes im Rückstellraum 54, welcher Druck auch der Druck im Pumpeninnenraum ist, so lange der Verbindungskanal 112 geschlossen ist, so wird dann auch die Verbindung 48 zum Kanal 65 geöffnet, so daß bei geöffnetem elektrisch betätigtem Schaltventil 66 die Entlastung zum Entlastungsraum ermöglicht wird und in die lastabhängige Beeinflussung des Pumpeninnenraumdruckes erfolgt. Auf diese Art und Weise wird die Zuschaltung der lastabhängigen Beeinflussung des Pumpeninnenraumdruckes in realer Abhängigkeit von dem Erreichen eines Zustandes der Brennkraftmaschine bei dem eine besondere Spritzbeginnverstellung nicht erforderlich ist, gesteuert. Insbesondere wird dabei aber grundsätzlich die lastabhängige Beeinflussung des Innenraumdruckes dann ermöglicht, wenn die erforderliche Betriebstemperatur erreicht ist und das Kugelrückschlagventil 156 ständig durch das Dehnstoffelement 59 abgehoben ist.In the embodiment according to FIG. 2, the shutdown of the load-dependent influencing of the pump interior pressure above the controlled discharge throttle 47 in the adjusting sleeve 24 with Helped by the slide valve member 61 with which the Setting mandrel 64 connected to actuate the valve member 56 was. With this configuration, the connection of the Line 48 to the relief chamber 44 completely in dependence controlled by temperature. Further configuration according to Figure 3 is now the control of this shutdown Lock channel 48 in the function of Ball check valve 156, 161, 157 occupied. That in Figure 2 as a simple check valve with a valve member in the form a ball 56 is now replaced by a combination this with a slide valve member 161, the one Has circumferential groove. About this slide valve member the ball 156 by the closing force, the compression spring 157, in Closing direction applied. In this position it has Slider valve member 161, which is in a cylinder bore slides, the connection through this cylinder bore 48 to the further line 65, in which the switching valve 66 is arranged, closed. Now open that Ball check valve either under the influence of increasing pressure in the reset space 54, which pressure too the pressure inside the pump is as long as the Connection channel 112 is closed, then the Connection 48 to channel 65 opened so that when open electrically operated switching valve 66 the discharge to Relief space is enabled and in the load-dependent Influence of the pump interior pressure takes place. To this Way is the connection of the load-dependent Influence of the pump interior pressure in real Dependence on reaching a state of Internal combustion engine with a special one Injection start adjustment is not required, controlled. In particular, however, the load-dependent is basically Influencing the interior pressure allows when the required operating temperature is reached and that Ball check valve 156 constantly through the expansion element 59 is lifted off.

Eine andere Ausgestaltung einer solchen Beeinflussung zeigt die Ausführungsform nach Figur 4. Dort ist zunächst eine erste Drucksteuereinrichtung derart vorgesehen, wie sie als Drucksteuereinrichtung 49 in Figur 2 gezeigt ist. Abweichend von dieser ist nun bei der Drucksteuereinrichtung 249 gemäß Figur 4 ein Kolbenschieber 100 vorgesehen der in einer Zylinderbohrung 101 verschiebbar angeordnet ist und auf seiner einen Seite von einer Rückstellfeder 103 beaufschlagt wird während seine andere Stirnseite in der geschlossenen Zylinderbohrung 101 einen Arbeitsraum 102 einschließt, der ständig mit der Entlastungsleitung 46 bzw. dem Rückstellraum 54 verbunden ist. Durch den Druck in diesem Rückstellraum kann der Kolbenschieber gegen die Kraft der Rückstellfeder 103 bis zur Anlage an einen Anschlag 104 verschoben werden derart, daß die durch die Zylinderbohrung 101 führende Verbindungsleitung zur weiterführenden Leitung durch den Kolbenschieber verschlossen ist. Sinkt der Druck im Rückstellraum 54 auf seinen den Normalbetrieb der Brennkraftmaschine kennzeichnenden Wert ab d.h. ist entweder durch das Dehnstoffelement 59 das von Figur 2 bereits bekannte Kugelrückschlagventil 256 geöffnet oder das Begrenzungsventil 106 durch den zunehmenden Pumpeninnenraumdruck geöffnet, so wird auch der Arbeitsraum 102 entlastet und die Verbindung zwischen der Verbindungsleitung 48 und der Leitung 65 zum Entlastungsraum 44 bei geöffnetem elektrisch betätigtem Schaltventil 66 hergestellt. Mit dieser Ausgestaltung kann nun ebenfalls die lastabhängige Beeinflussung des Pumpeninnenraumdruckes an einen Zustand angepaßt werden, der kennzeichnend dafür ist, daß eine besondere Spritzbeginnverstellung an die insbesondere für den nichtbetriebswarmen Bereich der Brennkraftmaschine notwendig ist, nicht mehr erforderlich ist. Dies kann bei noch nicht ganz betriebswarmer Brennkraftmaschine aber bei höherer Drehzahl der Fall sein oder es ist für die Zustände gültig, bei der die Brennkraftmaschine ihre Betriebstemperatur erreicht hat und das Kugelrückschlagventil 256 in Folge der Betätigung des Dehnstoffelements bzw. des temperaturabhängigen Stellglieds geöffnet ist.Another embodiment of such an influence shows the embodiment of Figure 4. There is first one first pressure control device provided as such as Pressure control device 49 is shown in Figure 2. Deviating of this is now in accordance with the pressure control device 249 Figure 4 is a piston valve 100 provided in a Cylinder bore 101 is slidably arranged and on one side is acted upon by a return spring 103 is closed while its other end face Cylinder bore 101 includes a working space 102 that constantly with the relief line 46 or the reset room 54 is connected. Because of the pressure in this recovery room the spool can move against the force of the return spring 103 to be moved up to a stop 104 such that the leading through the cylinder bore 101 Connection line to the continuing line through the Piston slide is closed. Does the pressure drop in the Reset room 54 on its normal operation Internal combustion engine characteristic value from i.e. is either by the expansion element 59 that of Figure 2 already known ball check valve 256 opened or that Limiting valve 106 by the increasing Pump interior pressure is opened, so is the work space 102 relieved and the connection between the Connection line 48 and line 65 to the relief chamber 44 when the electrically operated switching valve 66 is open manufactured. With this configuration, the load-dependent influencing of the pump interior pressure a condition that is indicative of that a special spray start adjustment to the especially for the non-warm area of the Internal combustion engine is necessary, no longer required is. This can happen if it is not yet warmer Internal combustion engine to be the case at a higher speed or it is valid for the states in which the Internal combustion engine has reached its operating temperature and the ball check valve 256 as a result of the actuation of the Expansion element or the temperature-dependent actuator is open.

Claims (6)

  1. Fuel injection pump for internal combustion engines with a pump piston (1) which is actuated by a cam drive, consisting of a rotating part (2) driven by a drive shaft (3) and of an at least essentially stationary part (6), one of which carries a cam track (4) which is moved relative to the other part and which serves for generating a reciprocating movement of the pump piston (1) coupled to one of the parts, the said reciprocating movement taking place transversely relative to the cam track, and with a start-of-injection timing piston (32) for adjusting one of the parts in or opposite to the direction of movement of the cam track (4), the said start-of-injection timing piston (32) being actuated counter to a return force (34) by a control pressure of a hydraulic pressure medium in a pump interior (12) of the fuel injection pump, the control pressure being provided by a feed pump (38) driven synchronously with the engine speed relative to the fuel injection pump, and being set by a first pressure control device (49) having a pressure control valve (39), the control member (40) of which controls an outflow (43) from the pump interior (12) and is loaded counter to the force of a spring (42) by the fed-in pressure prevailing in a return space (54) which is limited by the control member (40) and which is connected via a throttle (45) to the pump interior (12), the control pressure additionally being set by a second pressure control device (50) which has an outflow throttle (47), capable of being set in dependence on the load of the internal combustion engine, in a connection (48) between the pump interior (12) and the relief space (44), the said connection containing preferably a switching valve (66) controllable in dependence on operating parameters, and the return space (54) additionally having an outflow which leads to the relief space (44) and which can be controlled by a valve (52, 152, 252) which is controlled in dependence on a control variable characterizing the temperature of the internal combustion engine and as a result of the actuation of which there is adjusted indirectly or directly a valve member (61, 161, 100) of a valve, by means of which the connection (48) between the outflow throttle (47) and the relief space (44) of the second pressure control device (50) is controlled in such a way that, with the controlled valve (52, 152, 252) opened, the connection is opened, the preferably switching valve (66) being capable of being switched in dependence on parameters other than the temperature of the internal combustion engine, characterized in that there is provided, in parallel with the controlled valve (52, 152, 252), a limiting valve (106) which can be controlled in dependence on the control pressure in the pump interior and by means of which a connection can be made between the return space (54) and relief space (44) when the pressure in the pump interior exceeds a specific value.
  2. Fuel injection pump according to Claim 1, characterized in that the limiting valve (106) has, as a valve member, a slide (107) which limits a working space (109) connected via a throttle (108) to the pump interior and which can be adjusted to counter an adjustable return force (110).
  3. Fuel injection pump according to Claim 1 or 2, characterized in that the controlled valve (52) is a pressure-holding valve, the valve member (56) of which is loaded by a spring (57) and can be pushed open by an actuating member (64) adjustable according to the control variable, and a slide-valve member (61) can be adjusted at the same time as the actuation of the controlled valve, the said slide-valve member controlling the connection (48, 65) between the outflow throttle (47) and the relief space (44) of the second pressure control device (50) (Figure 1).
  4. Fuel injection pump according to Claim 1 or 2, characterized in that the controlled valve (152) is a pressure-holding valve, the valve member (156) of which is loaded by a spring (157) and can be pushed open by an actuating member (164) adjustable according to the control variable, and a slide-valve member (161) can be adjusted by means of the valve member, the said slide-valve member controlling the connection (48, 65) between the outflow throttle (47) and the relief space (44) of the second pressure control device (50) (Figure 2).
  5. Fuel injection pump according to Claim 4, characterized in that the valve member of the pressure-holding valve is a ball which cooperates with the valve seat (70) and which, on its side facing away from the valve seat, comes to bear on the slide-valve member (161) which, in turn, is loaded by the spring (157) (Figure 3).
  6. Fuel injection pump according to Claim 4, characterized in that the controlled valve (252) is a pressure-holding valve, the valve member (256) of which is loaded by a spring (257) and can be pushed open by an actuating member (264) adjustable according to the control variable, and the valve switching the connection (48, 65) has, as a valve member, a piston slide (100) which, in a cylinder (101) located in the connection (48, 65) between the outflow throttle (47) and relief space (44), limits a working space (102) constantly connected to the return space (54) and can be displaced by the pressure in the working space (102), counter to the force of the return spring (103), as far as a fixed stop (104), at which it has closed the connection (48, 65) between the outflow throttle (47) and the relief space (44) (Figure 4).
EP96934435A 1995-12-28 1996-10-24 Fuel-injection pump for internal-combustion engines Expired - Lifetime EP0812384B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19549046 1995-12-28
DE19549046A DE19549046A1 (en) 1995-12-28 1995-12-28 Fuel injection pump for internal combustion engines
PCT/DE1996/002014 WO1997024519A1 (en) 1995-12-28 1996-10-24 Fuel-injection pump for internal-combustion engines

Publications (2)

Publication Number Publication Date
EP0812384A1 EP0812384A1 (en) 1997-12-17
EP0812384B1 true EP0812384B1 (en) 2001-09-26

Family

ID=7781595

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96934435A Expired - Lifetime EP0812384B1 (en) 1995-12-28 1996-10-24 Fuel-injection pump for internal-combustion engines

Country Status (8)

Country Link
EP (1) EP0812384B1 (en)
JP (1) JPH11501384A (en)
KR (1) KR100304474B1 (en)
CN (1) CN1079896C (en)
BR (1) BR9607437A (en)
DE (2) DE19549046A1 (en)
RU (1) RU2166658C2 (en)
WO (1) WO1997024519A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9725415D0 (en) * 1997-12-02 1998-01-28 Lucas Ind Plc Advance arrangement
CN100436808C (en) * 2003-04-01 2008-11-26 Avl里斯脱有限公司 Internal combustion engine with piston injection pump

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3822257A1 (en) * 1988-07-01 1990-01-04 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE4341932A1 (en) * 1993-12-09 1995-06-14 Bosch Gmbh Robert Fuel injection pump for internal combustion engines

Also Published As

Publication number Publication date
JPH11501384A (en) 1999-02-02
WO1997024519A1 (en) 1997-07-10
RU2166658C2 (en) 2001-05-10
DE59607780D1 (en) 2001-10-31
KR100304474B1 (en) 2001-11-30
CN1175993A (en) 1998-03-11
EP0812384A1 (en) 1997-12-17
DE19549046A1 (en) 1997-07-03
BR9607437A (en) 1998-05-26
CN1079896C (en) 2002-02-27
KR19980702579A (en) 1998-07-15

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