EP0864037A1 - Fuel injection pump with a timing-device piston for timing beginning of injection - Google Patents

Fuel injection pump with a timing-device piston for timing beginning of injection

Info

Publication number
EP0864037A1
EP0864037A1 EP97930329A EP97930329A EP0864037A1 EP 0864037 A1 EP0864037 A1 EP 0864037A1 EP 97930329 A EP97930329 A EP 97930329A EP 97930329 A EP97930329 A EP 97930329A EP 0864037 A1 EP0864037 A1 EP 0864037A1
Authority
EP
European Patent Office
Prior art keywords
piston
injection
pressure
fuel injection
control
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.)
Granted
Application number
EP97930329A
Other languages
German (de)
French (fr)
Other versions
EP0864037B1 (en
Inventor
Wolfgang Fehlmann
Thomas Kulder
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0864037A1 publication Critical patent/EP0864037A1/en
Application granted granted Critical
Publication of EP0864037B1 publication Critical patent/EP0864037B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • 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
    • 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
    • F02M41/10—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 pump pistons acting as the distributor
    • F02M41/12—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 pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—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 pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/128—Varying injection timing by angular adjustment of the face-cam or the rollers support
    • 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 according to the preamble of claim 1.
  • a fuel injection pump which is known from DE-Al-35 32 719
  • an axially parallel blind hole extending from the end of the injection adjusting piston facing the working chamber is provided as a connecting line between the working chamber and the cylinder bore, the end hole being cut by a transverse bore running radially from the outside to the cylinder bore becomes.
  • the cross section of this transverse bore at the entrance to the cylinder bore has a circular area.
  • the fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage that initially only a small cross-sectional area is opened in the case of relative displacements of the control slide, which is smaller for the same actuating travel than the cross-sectional area that is usually established with a circular entry cross section of the connecting line into the cylinder bore .
  • a quick, violent reaction of the injection adjustment piston to the brief misalignment of the control slide is thus eliminated in such a way that such oscillating misalignments cannot increasingly rock to a further oscillation of the injection adjustment piston.
  • This pressure space which is accommodated outside the injection adjustment piston, decouples this pressure space from the pressure fluctuations in the working space of the injection adjustment piston, in particular through the relief space located between the two. In addition to the above embodiment according to claim 1, this also contributes to the reduction of pressure vibrations of the injection adjusting piston.
  • FIG. 1 shows a section through a power-fuel injection pump of the distributor type with radial pump pistons and a device for adjusting the start of injection in the embodiment according to the invention.
  • the fuel injection pumps of the distributor type can either be provided as pumps with an axially driven pump piston serving both as a distributor and as a pump piston, or radial pistons can be provided which deliver radially into a delivery channel arranged in a distributor.
  • a so-called radial piston pump of the known type is shown in section in FIG. 1.
  • Four pump pistons 1 are provided, which are at the same angular distance in a common radial plane
  • ER AL Axis of the distributor 2 are mounted in radial bores 3 of the distributor 2 such that they can be moved tightly. On one end, they enclose a common pump work chamber 4, which is filled with fuel in a known manner (not shown here) during the radial outward stroke of the pump piston 1 and during the radial inward stroke of the pump piston via a pressure line, likewise not recognizable here, with a distributor opening on the lateral surface of the distributor 2 is connected, the distributor opening controlling outgoing injection lines on the periphery of the distributor, one of which is supplied with fuel brought to the injection pressure when the pump piston moves inward.
  • the distributor is rotatably driven by a drive shaft by means not shown in such a way that on the one hand the distributor opening can perform its control function and on the other hand the pump pistons are moved in the circumferential direction.
  • Roller plungers 6, which follow a cam track 7, are located on the side of the pump piston opposite the pump working chamber 4, which follow a cam track 7 which is arranged on a cam ring 8 on its annular surface facing inwards to the distributor.
  • the cam ring 8 represents the substantially stationary part of the cam drive of the pump piston. While the device moving the pump piston, the z. B. the roller tappet 6 leading ring 9, which is coupled to the drive shaft, the moving part of the
  • the cam ring 8 has a nose 14 which engages in a recess 15 in an injection adjusting piston 16 on its cylindrical outer surface.
  • the injection adjustment piston is tightly displaceable in a cylinder 17 and encloses a working space 20 with its one end face 18 with the closed end of the cylinder 17 and a spring chamber 22 with its opposite, other end face in the cylinder, which is likewise closed there.
  • a return spring 23 is arranged, which is supported on the one hand on a closure part 24 closing the cylinder 17 and on the other hand on the end face 21 of the adjusting piston 16, and is thus clamped, the end of the injection piston 16 with its one end face 18 in contact with the Bring cylinder 17 opposite closing wall 25.
  • an axial blind bore 27 is also provided as a cylinder bore guiding a control slide 28, which opens towards the spring chamber 22.
  • the control slide 28 used there encloses with its one end 29 with the closed end of the cylinder bore a space 30 in which a compression spring 36 axially loads the control slide and projects with its other end into the spring space 22, where it is acted upon by a control spring 31 which, on the other hand, is also supported on the closure part 24.
  • a connecting line 32 extends from the one end face 18 and opens radially into the cylinder bore in the area of the overlap through the control slide.
  • This opening can be closed by an annular collar 33 of the control slide, this annular collar being an annular groove 34 on the working space side of one Annular space 35 separates, a pressure medium inlet opening into the annular groove 34 and the annular space 35 opening into the spring space 22, which is relieved via a relief line, not shown.
  • the ring edges delimiting the ring collar are control edges, by means of which the relative displacement of the
  • the connecting line 32 is either connected via the annular groove 34 to the pressure medium inlet 39 or is relieved via the annular space 35 to the spring chamber 22.
  • the annular groove 34 is always in connection with the pressure medium inlet 39, which is supplied with pressure medium from a pressure storage space 40.
  • a fuel pump 41 with a pressure control valve 42 connected in parallel is used to supply the storage space, by means of which the pressure storage space is supplied in a known manner with a pressure which increases essentially as a function of speed with increasing speed of the fuel injection pump or the associated internal combustion engine.
  • the control spool is adjusted with the aid of a plunger 49, with which the control spool is coupled under the action of the compression spring 36 so that it comes into contact with the plunger 49 at the end of the control spool projecting into the spring chamber 22.
  • This extends coaxially to the axis of the adjusting piston 16 or the control slide 28 and enters on the side opposite the end face 21 of the control slide into an axial bore 52 provided in the closure part 24.
  • a closed working cylinder 53 is arranged in the closure part 24, which connects coaxially to the axial bore 52 and is closed at the other end by a cover 54.
  • a piston 55 formed at the end of the plunger 49 is displaceably arranged in the working cylinder and includes a pressure chamber 56 on its one side facing the spring chamber 22 and a pressure-relieving chamber 57 on the other side between the piston 55 and the cover 54. via an axial bore 44, which is in a transverse bore 45 merges and is constantly connected to the spring chamber.
  • a spring plate 58 is also connected to the plunger 49 in the area of the spring chamber, between which and the closure part 24 a control spring 31 is supported, against which the plunger 49 is displaced under the action of a control pressure introduced into the pressure chamber 56.
  • the above-mentioned speed-dependent pressure serves as control pressure.
  • the collar 33 performs a controlling function in such a way that the working space 20 is supplied with pressure medium until a subsequent movement of the adjusting piston 16 against the force of the spring 23 the connecting line 32, which was previously opened, is closed again. Conversely, when the pressure in the pressure chamber 56 drops, the work space 20 is relieved until the connecting line is closed again.
  • the pressure in the pressure chamber 56 can also be relieved or modified by a relief line 43 in which an electrically controlled valve 44 is seated.
  • the inlet 60 of the connecting line 39 into the cylinder bore 27 has an elongated, preferably elliptical cross section with the control slide located in the direction of displacement
  • Main extension provided so that when the control spool is displaced relative to the injection adjusting piston by the control edge of the collar, only a small, throttling cross-section is opened towards the working space 20. If vibrations occur, pressure medium can be supplied to or removed from the working space 20 only slightly. The tendency to vibrate in the event of disturbing forces, such as engine impacts, is thus significantly reduced.
  • other cross-sectional profiles that support this effect can also be realized at the opening of the inlet cross-section of the pressure medium inlet. Compound parabola branches or hyper branches or other limitations of the cross-sectional area are to be mentioned as conic section curves.
  • This configuration is particularly advantageous in connection with the pressure chamber 56 fixed to the housing, which is arranged outside the injection adjustment piston. With this arrangement, the occurrence of vibrations due to impacts transmitted by the cam drive is additionally avoided, since this pressure chamber via the relieved spring chamber from the shock-loaded pressure side and the resulting movements of the injection adjustment piston is decoupled.

Landscapes

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

Abstract

Disclosed is a fuel injection pump provided with a timing device piston (16) for timing beginning of injection and designed as a slaved piston for a slide valve (28) located therein. Said piston encompasses a working chamber (20) on one of its sides and is driven by pressure in said working chamber in opposition to the force of a return spring (23) and connected to a substantially fixed part of fuel injection pump cam drive. In order to avoid the effects of pressure backlash arising from kickback on the slide valve (28) and its setting, the inlet cross-section of connecting conduit is designed as an extended elongated cross-section which extends in the sliding direction of said slide valve. This enables trouble-free setting of the slide valve (28) and more precise vibration-free setting of timing device piston (16) and beginning of injection.

Description

Kraftstoffeinspritzpumpe mit einem der Spritzbeginn- verstellung dienenden SpritzverstellkolbenFuel injection pump with a spray adjustment piston that serves to adjust the start of injection
Stand der TechnikState of the art
Die Erfindung geht von einer Kraftstoffeinspritzpumpe gemäß der Gattung des Patentanspruchs 1 aus. Bei einer solchen, durch die DE-Al-35 32 719 bekannte Kraftstoffeinspritzpumpe ist als Verbindungsleitung zwischen Arbeitsraum und Zylinderbohrung eine von der dem Arbeitsraum zugewandten Stirnseite des Spritzverstellkolbens ausgehende achsparallele Sacklochbohrung vorgesehen, die an ihrem Ende von einer radial von außen zur Zylinderbohrung verlaufende Querbohrung geschnitten wird. Der Querschnitt dieser Querbohrung am Eintritt in die Zylinderbohrung hat eine Kreisfläche.The invention is based on a fuel injection pump according to the preamble of claim 1. In such a fuel injection pump, which is known from DE-Al-35 32 719, an axially parallel blind hole extending from the end of the injection adjusting piston facing the working chamber is provided as a connecting line between the working chamber and the cylinder bore, the end hole being cut by a transverse bore running radially from the outside to the cylinder bore becomes. The cross section of this transverse bore at the entrance to the cylinder bore has a circular area.
Bei einer solchen Spritzverstelleinrichtung tritt das Problem auf, daß es auf Grund der Lastwechsel im Nockenantrieb der Kraftstoffeinspritzpumpe zu Druckschwankungen im Bereich der Druckräume des Spritzverstellers bzw. zu Relativbewegungen zwischen Spritzverstellkolben und Steuerschieber kommt . Vorteile der ErfindungWith such a spray adjustment device, the problem arises that, due to the load changes in the cam drive of the fuel injection pump, pressure fluctuations occur in the area of the pressure adjuster of the injection adjuster or relative movements between the injection adjustment piston and the control slide. Advantages of the invention
Durch die erfindungsgemäße Kraftstoffeinspritzpumpe mit den kennzeichnenden Merkmalen des Patentanspruchs 1 ergibt sich der Vorteil, daß sich bei Relatiwerschiebungen des Steuerschiebers zunächst nur eine kleine Querschnittsfläche aufgesteuert wird, die bei gleichem Stellweg kleiner ist als die üblicherweise sich einstellende Querschnittsfläche bei kreisrundem Eintrittsquerschnitt der Verbindungsleitung in die Zylinderbohrung. Damit wird dann, wenn auf Grund der Relativbewegung zwischen Spritzverstellkolben und Steuerschieber der Steuerschieber kurzzeitig aus seiner an sich richtigen Position relativ zum Spritzverstellkolben verstellt wird nur ein sehr kleiner, drosselnder Querschnitt aufgesteuert, so daß sich die Fehleinstellung des Steuerschiebers nicht sofort in Form einer wesentlichen Druckänderung im Arbeitsraum des Spritzverstellkolbens auswirkt. Damit entfällt eine schnelle, heftige Reaktion des Spritzverstellkolbens auf die kurzzeitige Fehlstellung des Steuer- Schiebers derart, daß sich solche schwingenden Fehlstellungen nicht verstärkt zu einem weiteren Schwingen des Spritz- verstellkolbens aufschaukeln können.The fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage that initially only a small cross-sectional area is opened in the case of relative displacements of the control slide, which is smaller for the same actuating travel than the cross-sectional area that is usually established with a circular entry cross section of the connecting line into the cylinder bore . This means that if, due to the relative movement between the injection adjustment piston and the control slide, the control slide is briefly adjusted from its proper position relative to the injection adjustment piston, only a very small, restricting cross-section is opened, so that the incorrect adjustment of the control slide does not immediately take the form of a significant pressure change in the working area of the injection adjustment piston. A quick, violent reaction of the injection adjustment piston to the brief misalignment of the control slide is thus eliminated in such a way that such oscillating misalignments cannot increasingly rock to a further oscillation of the injection adjustment piston.
In den Unteransprüchen sind vorteilhafte Weiterbildungen der Ausgestaltung des Eintrittsquerschnitts der Verbindungsleitung in die Zylinderbohrung angegeben. Wesentlich ist dabei, einen quasi kontinuierlichen Querschnittsverlauf bei stetiger Verstellung der diesen Querschnitt steuernden Steuerkante zu erzielen, wobei die Zunahme des Querschnitts über einen relativ langen Verstellweg allmählich erfolgt. In geöffneter Stellung steht dann der volle Überströmquerschnitt zur Verfügung, so daß bei gewollter Verstellung des Steuerschiebers mit der erforderlichen Schnelligkeit eine Korrektur der Spritzverstellkolbenstellung erfolgen kann. In weiterhin vorteilhafter Ausgestaltung gemäß Patentanspruch 5 erfolgt die Verstellung des Steuerschiebers in an sich bekannter Weise durch ein Stellglied, das in einem gehäusefesten Teil des Spritzverstellers einen Druckraum einschließt mit einer vom Steuerdruck beaufschlagten Fläche. Durch diesen außerhalb des Spritzverstellkolbens untergebrachten Druckraum erfolgt eine Entkopplung dieses Druckraumes von den Druckschwankungen im Arbeitsraum des Spritzverstellkolbens insbesondere durch den zwischen beiden liegenden Entlastungsraum. Auch dies trägt in Ergänzung zur obigen Ausgestaltung nach Patentanspruch 1 zur Reduzierung von Druckschwingungen des Spritzverstellkolbens bei.Advantageous further developments of the configuration of the inlet cross section of the connecting line into the cylinder bore are specified in the subclaims. It is essential here to achieve a quasi-continuous cross-sectional profile with constant adjustment of the control edge controlling this cross-section, the cross-section gradually increasing over a relatively long adjustment path. The full overflow cross section is then available in the open position, so that when the control spool is deliberately adjusted, the spray adjustment piston position can be corrected with the required speed. In a further advantageous embodiment according to claim 5, the control slide is adjusted in a manner known per se by an actuator which encloses a pressure chamber in a part of the injection adjuster fixed to the housing with an area acted upon by the control pressure. This pressure space, which is accommodated outside the injection adjustment piston, decouples this pressure space from the pressure fluctuations in the working space of the injection adjustment piston, in particular through the relief space located between the two. In addition to the above embodiment according to claim 1, this also contributes to the reduction of pressure vibrations of the injection adjusting piston.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird in der nachfolgenden Beschreibung näher erläutert. Es zeigt Figur 1 einen Schnitt durch eine Kraf - Stoffeinspritzpumpe der Verteilerbauart mit radial liegenden Pumpenkolben und einer Einrichtung zur Spritzbeginnverstellung in der erfindungsgemäßen Ausgestaltung.An embodiment of the invention is shown in the drawing and is explained in more detail in the following description. FIG. 1 shows a section through a power-fuel injection pump of the distributor type with radial pump pistons and a device for adjusting the start of injection in the embodiment according to the invention.
Beschreibung des AusführungsbeispielsDescription of the embodiment
Die 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 einen in einem Verteiler angeordneten Förderkanal fördern. Eine solche sogenannte Radialkolbenpumpe der bekannten Bauart ist im Schnitt in Figur 1 dargestellt. Dabei sind vier Pumpenkolben 1 vorgesehen, die im gleichen Winkelabstand in einer gemeinsamen Radialebene zurThe fuel injection pumps of the distributor type can either be provided as pumps with an axially driven pump piston serving both as a distributor and as a pump piston, or radial pistons can be provided which deliver radially into a delivery channel arranged in a distributor. Such a so-called radial piston pump of the known type is shown in section in FIG. 1. Four pump pistons 1 are provided, which are at the same angular distance in a common radial plane
ER A L Achse des Verteilers 2 in Radialbohrungen 3 des Verteilers 2 dicht verschiebbar gelagert sind. Auf ihrer einen Stirnseite schließen sie einen gemeinsamen Pumpenarbeitsraum 4 ein, der in bekannter, hier nicht weiter gezeigten Weise beim Radial- auswärtshub der Pumpenkolben 1 mit Kraftstoff gefüllt wird und beim Radialeinwärtshub der Pumpenkolben über eine hier ebenfalls nicht erkennbare Druckleitung mit einer Verteileröffnung an der Mantelfläche des Verteilers 2 verbunden wird, wobei die Verteileröffnung am Umfang des Verteilers abgehende Einspritzleitungen ansteuert, von denen jeweils eine bei einwärts bewegten Pumpenkolben mit auf Einspritz- druck gebrachten Kraftstoff versorgt wird. Der Verteiler ist dabei durch nicht weiter gezeigte Mittel von einer Antriebswelle rotierend angetrieben derart, daß einerseits die Verteileröffnung ihre Steuerfunktion ausführen kann und andererseits die Pumpenkolben in Umfangsrichtung bewegt werden. Dabei liegen an der dem Pumpenarbeitsraum 4 gegenüberliegenden Seite der Pumpenkolben Rollenstößel 6 an, die einer Nockenbahn 7 folgen, die auf einem Nockenring 8 an dessen einwärts zum Verteiler weisenden Ringfläche angeordnet ist. Der Nockenring 8 stellt den im wesentlichen stillstehenden Teil des Nockenantriebs der Pumpenkolben dar. Während die die Pumpenkolben bewegende Einrichtung, die z. B. der die Rollenstößel 6 führende Ring 9 sein kann, der mit der Antriebswelle gekoppelt ist, den bewegten Teil desER AL Axis of the distributor 2 are mounted in radial bores 3 of the distributor 2 such that they can be moved tightly. On one end, they enclose a common pump work chamber 4, which is filled with fuel in a known manner (not shown here) during the radial outward stroke of the pump piston 1 and during the radial inward stroke of the pump piston via a pressure line, likewise not recognizable here, with a distributor opening on the lateral surface of the distributor 2 is connected, the distributor opening controlling outgoing injection lines on the periphery of the distributor, one of which is supplied with fuel brought to the injection pressure when the pump piston moves inward. The distributor is rotatably driven by a drive shaft by means not shown in such a way that on the one hand the distributor opening can perform its control function and on the other hand the pump pistons are moved in the circumferential direction. Roller plungers 6, which follow a cam track 7, are located on the side of the pump piston opposite the pump working chamber 4, which follow a cam track 7 which is arranged on a cam ring 8 on its annular surface facing inwards to the distributor. The cam ring 8 represents the substantially stationary part of the cam drive of the pump piston. While the device moving the pump piston, the z. B. the roller tappet 6 leading ring 9, which is coupled to the drive shaft, the moving part of the
Nockenantriebs darstellen. Je nach Stellung des Nockenrings, der mit seiner zylindrischen Außenwand in einer entsprechenden zylindrischen Ausnehmung 10 des Pumpengehäuses 11 der Kraftstoffeinspritzpumpe geführt ist, wird ein früheres oder späteres Auflaufen der Rollen 12 der Rollenstößel 6 auf die jeweiligen Nocken 13 bewirkt, die so angeordnet sind, daß alle Rollenstößel synchron einwärts oder auswärts um die gleichen Hübe bewegt werden. Mit der Verstellung des Nockenrings wird somit der Beginn des Förderhubs der Pumpenkolben und damit der Spritzbeginn im Verhältnis zum Antrieb der Kraftstoffeinspritzpumpe verändert .Represent cam drive. Depending on the position of the cam ring, which is guided with its cylindrical outer wall in a corresponding cylindrical recess 10 of the pump housing 11 of the fuel injection pump, an earlier or later emergence of the rollers 12 of the roller tappet 6 is effected on the respective cams 13, which are arranged such that all roller tappets are moved synchronously inwards or outwards by the same strokes. With the adjustment of the cam ring, the start of the delivery stroke of the pump piston is thus and thus the start of injection changes in relation to the drive of the fuel injection pump.
Zur Verstellung weist der Nockenring 8 eine Nase 14 auf, die in eine Ausnehmung 15 in einem Spritzverstellkolben 16 an dessen zylindrischer Mantelfläche eingreift. Der Spritzverstellkolben ist in einem Zylinder 17 dicht verschiebbar und schließt mit seiner einen Stirnseite 18 mit dem geschlossenen Ende des Zylinders 17 einen Arbeitsraum 20 ein und mit seiner gegenüberliegenden, anderen Stirnfläche im dort ebenfalls verschlossenen Zylinder einen Federraum 22 ein. In diesem ist eine Rückstellfeder 23 angeordnet, die sich einerseits an einem den Zylinder 17 verschließenden Verschlußteil 24 und andererseits an der Stirnseite 21 des Verstell- kolbens 16 abstützt und so eingespannt bestrebt ist, den Spritzverstellkolben 16 mit seiner einen Stirnseite 18 in Anlage an die den Zylinder 17 gegenüberliegend verschließenden Wand 25 zu bringen.For adjustment, the cam ring 8 has a nose 14 which engages in a recess 15 in an injection adjusting piston 16 on its cylindrical outer surface. The injection adjustment piston is tightly displaceable in a cylinder 17 and encloses a working space 20 with its one end face 18 with the closed end of the cylinder 17 and a spring chamber 22 with its opposite, other end face in the cylinder, which is likewise closed there. In this, a return spring 23 is arranged, which is supported on the one hand on a closure part 24 closing the cylinder 17 and on the other hand on the end face 21 of the adjusting piston 16, and is thus clamped, the end of the injection piston 16 with its one end face 18 in contact with the Bring cylinder 17 opposite closing wall 25.
Im Spritzverstellkolben 16 ist ferner eine axiale Sackbohrung 27 als eine einen Steuerschieber 28 führende Zylinderbohrung vorgesehen, die sich zum Federraum 22 hin öffnet. Der dort eingesetzte Steuerschieber 28 schließt mit seiner einen Stirnseite 29 mit dem geschlossenen Ende der Zylinderbohrung einen Raum 30 ein, in dem eine Druckfeder 36 den Steuerschieber axial belastet und ragt mit seinem anderen Ende in den Federraum 22, wo er von einer Steuerfeder 31 beaufschlagt ist, die sich andererseits ebenfalls am Verschlußteil 24 abstützt. Parallel zur Zylinderbohrung 27 verläuft im Stellkolben eine von der einen Stirnseite 18 ausgehende Verbindungsleitung 32, die radial im Bereich der Überdeckung durch den Steuerschieber in die Zylinderbohrung einmündet. Diese Einmündung kann durch einen Ringbund 33 des Steuerschiebers verschlossen werden, wobei dieser Ringbund eine arbeitsraumseitig liegende Ringnut 34 von einem Ringraum 35 trennt, wobei in die Ringnut 34 ein Druckmittel- Zulauf einmündet und der Ringraum 35 in den Federraum 22 mündet, der über eine nicht gezeigte Entlastungsleitung entlastet ist. Die den Ringbund begrenzenden Ringkanten sind Steuerkanten, durch die bei einer Relatiwerschiebung desIn the injection adjusting piston 16, an axial blind bore 27 is also provided as a cylinder bore guiding a control slide 28, which opens towards the spring chamber 22. The control slide 28 used there encloses with its one end 29 with the closed end of the cylinder bore a space 30 in which a compression spring 36 axially loads the control slide and projects with its other end into the spring space 22, where it is acted upon by a control spring 31 which, on the other hand, is also supported on the closure part 24. Parallel to the cylinder bore 27, a connecting line 32 extends from the one end face 18 and opens radially into the cylinder bore in the area of the overlap through the control slide. This opening can be closed by an annular collar 33 of the control slide, this annular collar being an annular groove 34 on the working space side of one Annular space 35 separates, a pressure medium inlet opening into the annular groove 34 and the annular space 35 opening into the spring space 22, which is relieved via a relief line, not shown. The ring edges delimiting the ring collar are control edges, by means of which the relative displacement of the
Steuerschiebers die Verbindungsleitung 32 entweder über die Ringnut 34 mit dem Druckmittelzulauf 39 verbunden oder über den Ringraum 35 zum Federraum 22 entlastet wird. Dabei ist die Ringnut 34 ständig in Verbindung mit dem Druckmittel- zulauf 39, der von einem Druckspeicherraum 40 mit Druckmittel versorgt wird. Zur Versorgung des Speicherraums dient eine Kraftstoffpumpe 41 mit parallel geschaltetem Drucksteuerventil 42, durch die zusammen der Druckspeicherraum in bekannter Weise mit einem Druck versorgt wird, der im wesentlichen drehzahlabhängig mit zunehmender Drehzahl der Kraftstoffeinspritzpumpe bzw. der zugehörigen Brennkraftmaschine steigt.Control slide the connecting line 32 is either connected via the annular groove 34 to the pressure medium inlet 39 or is relieved via the annular space 35 to the spring chamber 22. The annular groove 34 is always in connection with the pressure medium inlet 39, which is supplied with pressure medium from a pressure storage space 40. A fuel pump 41 with a pressure control valve 42 connected in parallel is used to supply the storage space, by means of which the pressure storage space is supplied in a known manner with a pressure which increases essentially as a function of speed with increasing speed of the fuel injection pump or the associated internal combustion engine.
Die Verstellung des Steuerschiebers erfolgt mit Hilfe eines Stößels 49, mit dem der Steuerschieber unter Einwirkung der Druckfeder 36 gekoppelt ist so daß er am in den Federraum 22 ragenden Ende des Steuerschiebers am Stößel 49 zur Anlage kommt. Dieser erstreckt sich koaxial zur Achse des Verstellkolben 16 bzw. des Steuerschieber 28 und tritt auf der der Stirnseite 21 des Steuerschieber gegenüberliegend Seite in eine im Verschlußteil 24 vorgesehene axiale Bohrung 52 ein. In dem Verschlußteil 24 ist ein geschlossener Arbeitszylinder 53 angeordnet, der sich koaxial an die axiale Bohrung 52 anschließt und anderen Endes durch einen Deckel 54 verschlossen ist. In dem Arbeitszylinder ist ein am Ende des Stößels 49 ausgebildeter Kolben 55 verschiebbar angeordnet, der auf seiner einen, zum Federraum 22 weisenden Seite einen Druckraum 56 und auf seiner anderen Seite zwischen dem Kolben 55 und dem Deckel 54 einen entlasteten Raum 57 ein- schließt, der über einen Axialbohrung 44, die in eine Quer- bohrung 45 übergeht und mit dem Federraum ständig verbunden ist. Mit dem Stößel 49 ist im Bereich des Federraumes ferner ein Federteller 58 verbunden, zwischen dem und dem Verschlußteil 24 sich eine Steuerfeder 31 abstützt, gegen die der Stößel 49 unter Einwirkung eines in den Druckraum 56 eingebrachten Steuerdruckes verschoben wird. Als Steuerdruck dient der obengenannte drehzahlabhängige Druck.The control spool is adjusted with the aid of a plunger 49, with which the control spool is coupled under the action of the compression spring 36 so that it comes into contact with the plunger 49 at the end of the control spool projecting into the spring chamber 22. This extends coaxially to the axis of the adjusting piston 16 or the control slide 28 and enters on the side opposite the end face 21 of the control slide into an axial bore 52 provided in the closure part 24. A closed working cylinder 53 is arranged in the closure part 24, which connects coaxially to the axial bore 52 and is closed at the other end by a cover 54. A piston 55 formed at the end of the plunger 49 is displaceably arranged in the working cylinder and includes a pressure chamber 56 on its one side facing the spring chamber 22 and a pressure-relieving chamber 57 on the other side between the piston 55 and the cover 54. via an axial bore 44, which is in a transverse bore 45 merges and is constantly connected to the spring chamber. A spring plate 58 is also connected to the plunger 49 in the area of the spring chamber, between which and the closure part 24 a control spring 31 is supported, against which the plunger 49 is displaced under the action of a control pressure introduced into the pressure chamber 56. The above-mentioned speed-dependent pressure serves as control pressure.
Bei einer bei steigendem Steuerdruck auftretenden Rechtsver- Schiebung des Steuerschiebers durch den Stößel 49 führt der Ringbund 33 eine steuernde Funktionen derart aus, daß der Arbeitsraum 20 mit Druckmittel versorgt wird so lange, bis durch eine nachfolgende Bewegung des Verstellkolbens 16 gegen die Kraft der Feder 23 die Verbindungsieitung 32, die zuvor geöffnet wurde, wieder verschlossen wird. Umgekehrt wird bei einem Sinken des Druckes im Druckraum 56 der Arbeitsraum 20 so lange entlastet, bis die Verbindungs- leitung wieder verschlossen ist. Der Druck im Druckraum 56 kann dabei noch durch eine Entlastungsleitung 43, in der ein elektrisch gesteuertes Ventil 44 sitzt, entlastet bzw. modifiziert werden.In the event of a rightward shift of the control spool by the tappet 49 as the control pressure increases, the collar 33 performs a controlling function in such a way that the working space 20 is supplied with pressure medium until a subsequent movement of the adjusting piston 16 against the force of the spring 23 the connecting line 32, which was previously opened, is closed again. Conversely, when the pressure in the pressure chamber 56 drops, the work space 20 is relieved until the connecting line is closed again. The pressure in the pressure chamber 56 can also be relieved or modified by a relief line 43 in which an electrically controlled valve 44 is seated.
Bei dieser bekannten Einrichtung zur Spritzbeginnverstellung tritt das Problem auf, daß über die Rollen 12 beim Antrieb der Pumpenkolben rückwirkende Kräfte auf den Nockenring 8 übertragen werden, die wiederum auf den Spritzverstellkolben 16 weitergeleitet werden so daß der Druck im Arbeitsraum 20 stoßweise erhöht wird. Dieser Druck steht dann auch am Ringbund 33 an, über den bei schwingenden Bewegungen des Steuerschiebers relativ zum Spritzverstellkolben Kraftstoff auch in den Raum 20 gelangen kann und dort zu Druckerhöhungen führt, die wieder Rückwirkungen auf die Stellung des Steuerschiebers haben. Das führt zu einem instabilen Verhalten des Spritzverstellkolbens bzw. der gesamten Einrichtung zur Spritzbeginnverstellung. Zur Vermeidung dieser Nachteile ist der Eintritt 60 der Verbindungsleitung 39 in die Zylinderbohrung 27 mit einem langgestreckten, vorzugsweise elliptischen Querschnitt mit in der Verschieberichtung des Steuerschiebers liegenderIn this known device for spray start adjustment, the problem arises that retroactive forces are transmitted to the cam ring 8 via the rollers 12 when driving the pump piston, which in turn are passed on to the spray adjustment piston 16 so that the pressure in the working chamber 20 is increased intermittently. This pressure is then also present at the collar 33, via which fuel can reach the space 20 when the control spool moves in relation to the injection adjustment piston and leads to pressure increases there, which in turn have repercussions on the position of the control spool. This leads to an unstable behavior of the injection adjustment piston or the entire device for the injection start adjustment. In order to avoid these disadvantages, the inlet 60 of the connecting line 39 into the cylinder bore 27 has an elongated, preferably elliptical cross section with the control slide located in the direction of displacement
Haupterstreckung versehen, so daß bei einer Verschiebung des Steuerschiebers relativ zum Spritzverstellkolben durch die Steuerkante des Ringbundes zunächst nur ein kleiner, drosselnder Querschnitt zum Arbeitsraum 20 hin aufgesteuert wird. So kann bei auftretenden Schwingungen dem Arbeitsraum 20 nur geringfügig Druckmittel zugeführt oder von diesem abgeführt werden. Die Schwingungsneigung bei auftretenden Störkräften, wie Triebwerksstößen, ist damit wesentlich verringert. Statt einem elliptischen Querschnitt können auch andere, diese Wirkung unterstützende Querschnittsverläufe an der Öffnung des Eintrittquerschnitt des Druckmittelzulaufes verwirklicht werden. Dazu sind zu nennen zusammengesetzte Parabeläste oder Hyperbeläste oder auch andere Begrenzungen der Querschnittsfläche als Kegelschnittkurven.Main extension provided so that when the control spool is displaced relative to the injection adjusting piston by the control edge of the collar, only a small, throttling cross-section is opened towards the working space 20. If vibrations occur, pressure medium can be supplied to or removed from the working space 20 only slightly. The tendency to vibrate in the event of disturbing forces, such as engine impacts, is thus significantly reduced. Instead of an elliptical cross-section, other cross-sectional profiles that support this effect can also be realized at the opening of the inlet cross-section of the pressure medium inlet. Compound parabola branches or hyper branches or other limitations of the cross-sectional area are to be mentioned as conic section curves.
Besonders vorteilhaft ist diese Ausgestaltung in Verbindung mit dem oben beschriebenen außerhalb des Spritzverstell- kolbens angeordneten gehäusefesten Druckraum 56. Mit dieser Anordnung wird zusätzlich das Auftreten von Schwingungen aufgrund von vom Nockenantrieb übertragenen Stößen vermieden, da dieser Druckraum über den entlasteten Federraum von der stoßbelasteten Druckseite und den resultierenden Bewegungen des Spritzverstellkolben entkoppelt ist. This configuration is particularly advantageous in connection with the pressure chamber 56 fixed to the housing, which is arranged outside the injection adjustment piston. With this arrangement, the occurrence of vibrations due to impacts transmitted by the cam drive is additionally avoided, since this pressure chamber via the relieved spring chamber from the shock-loaded pressure side and the resulting movements of the injection adjustment piston is decoupled.

Claims

Ansprüche Expectations
1. Kraftstoffeinspritzpumpe mit einem der Spritzbeginnverstellung dienenden Spritzverstellkolben (16) , der in einem Zylinder (17) einen Arbeitsraum (20) begrenzt, der von einem steuerbaren Druckmittel beaufschlagt ist, das den Spritzverstellkolben entgegen einer Rückstellkraft verstellt und mit einem in einer einseitig geschlossenen Zylinderbohrung (27) des Spritzverstellkolbens (16) in Achsrichtung des Spritzverstellkolbens (16) verschiebbar angeordneten Steuerschieber (28) , der von einem Steuerdruck entgegen der Kraft einer Steuerfeder (31) , verstellbar ist, und in der Zylinder- bohrung (27) mit Steuerkanten eine Verbindung einer Verbindungsleitung (32) von der Zylinderbohrung (27) zum Arbeitsraum (20) mit einem Druckmittelzulauf (39) in die Zylinderbohrung (27) oder einen Druckmittelablauf (35) aus der Zylinderbohrung und steuert, dadurch gekennzeichnet, daß der von der Steuerkante des Steuerschiebers (28) gesteuerte Eintrittsquerschnitt (60) der Verbindungsleitung (32) in die Zylinderbohrung (27) als ein sich in Verschieberichtung des Steuerschiebers erstreckender langgestreckter Querschnitt ausgebildet ist.1.Fuel injection pump with a spray adjustment piston (16) serving to start the injection, which delimits a working chamber (20) in a cylinder (17) which is acted upon by a controllable pressure medium which adjusts the injection adjustment piston against a restoring force and with a cylinder bore which is closed on one side (27) of the injection adjusting piston (16) which is displaceable in the axial direction of the injection adjusting piston (16) and which is adjustable by a control pressure against the force of a control spring (31), and in the cylinder bore (27) with control edges Connection of a connecting line (32) from the cylinder bore (27) to the work space (20) with a pressure medium inlet (39) into the cylinder bore (27) or a pressure medium outlet (35) from the cylinder bore and controls, characterized in that the from the control edge of the Control slide (28) controlled entry cross-section (60) of the connecting line (32) in the Cylinder bore (27) is designed as an elongated cross section extending in the direction of displacement of the control slide.
2. Kraftstoffeinspritzpumpe nach Anspruch 1, dadurch gekennzeichnet, daß der Querschnitt ellipsenförmig ausgebildet ist . 2. Fuel injection pump according to claim 1, characterized in that the cross section is elliptical.
3. Kraftstoffeinspritzpumpe nach Anspruch 1, dadurch gekennzeichnet, daß der Querschnitt parabolisch ausgebildet ist.3. Fuel injection pump according to claim 1, characterized in that the cross section is parabolic.
4. Kraftstoffeinspritzpumpe nach Anspruch 1, dadurch gekennzeichnet, daß der Querschnitt hyperbolisch ausgebildet ist.4. Fuel injection pump according to claim 1, characterized in that the cross section is hyperbolic.
5. Kraftstoffeinspritzpumpe nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß ein eine Verstellung des Steuerschiebers (28) bewirkendes Stellglied (49, 55), eine vom Steuerdruck beaufschlagte Fläche aufweist und das Stellglied (49, 55) mit dieser Fläche in einen in einem gehäusefesten Teil (24) angeordneten, vom Arbeitsraum (20) getrennten Druckraum (56) ragt und zwischen dem Druckraum (56) und dem Arbeitsraum (20) des Spritzverstellkolbens (16) ein Entlastungsraum (22) angeordnet ist, der von der Stirnseite (21) des Spritzverstellkolbens (16) begrenzt wird und der Arbeitsraum (20) auf der dem Entlastungsraum (22) gegenüberliegenden Seite des Spritzverstellkolbens (16) angeordnet ist. 5. Fuel injection pump according to one of the preceding claims, characterized in that an adjustment of the control slide (28) effecting actuator (49, 55) has a surface acted upon by the control pressure and the actuator (49, 55) with this surface in one Part (24) fixed to the housing and separated from the working space (20) protrudes pressure space (56) and between the pressure space (56) and the working space (20) of the injection adjusting piston (16) a relief space (22) is arranged, which is from the front side (21 ) of the injection adjustment piston (16) is limited and the working space (20) is arranged on the side of the injection adjustment piston (16) opposite the relief space (22).
EP97930329A 1996-10-02 1997-06-17 Fuel injection pump with a timing-device piston for timing beginning of injection Expired - Lifetime EP0864037B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19640678A DE19640678A1 (en) 1996-10-02 1996-10-02 Fuel injection pump with a spray adjustment piston that serves to adjust the start of injection
DE19640678 1996-10-02
PCT/DE1997/001225 WO1998014695A1 (en) 1996-10-02 1997-06-17 Fuel injection pump with a timing-device piston for timing beginning of injection

Publications (2)

Publication Number Publication Date
EP0864037A1 true EP0864037A1 (en) 1998-09-16
EP0864037B1 EP0864037B1 (en) 2002-03-20

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EP97930329A Expired - Lifetime EP0864037B1 (en) 1996-10-02 1997-06-17 Fuel injection pump with a timing-device piston for timing beginning of injection

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US (1) US6041760A (en)
EP (1) EP0864037B1 (en)
JP (1) JP2000501478A (en)
KR (1) KR100453752B1 (en)
CN (1) CN1079897C (en)
DE (2) DE19640678A1 (en)
HU (1) HU222147B1 (en)
WO (1) WO1998014695A1 (en)

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GB2367591B (en) * 1999-06-18 2004-03-03 Rotech Holdings Ltd Improved pump

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DE19849925A1 (en) * 1998-10-29 2000-05-04 Bosch Gmbh Robert Fuel injection pump
GB0303603D0 (en) * 2003-02-17 2003-03-19 Delphi Tech Inc Improvements in or relating to pressurisation pumps
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CN102305140B (en) * 2011-08-30 2014-06-11 潍柴动力股份有限公司 Fuel injector starting time measuring equipment and fuel injector

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DE3532719A1 (en) 1985-09-13 1987-03-26 Bosch Gmbh Robert 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
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Publication number Priority date Publication date Assignee Title
GB2367591B (en) * 1999-06-18 2004-03-03 Rotech Holdings Ltd Improved pump

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WO1998014695A1 (en) 1998-04-09
US6041760A (en) 2000-03-28
HU222147B1 (en) 2003-04-28
HUP9901493A3 (en) 2000-03-28
KR19990071634A (en) 1999-09-27
KR100453752B1 (en) 2004-12-23
EP0864037B1 (en) 2002-03-20
HUP9901493A2 (en) 1999-08-30
CN1079897C (en) 2002-02-27
DE19640678A1 (en) 1998-04-09
JP2000501478A (en) 2000-02-08
CN1205048A (en) 1999-01-13
DE59706678D1 (en) 2002-04-25

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