EP0900334B1 - Pressure valve - Google Patents

Pressure valve Download PDF

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Publication number
EP0900334B1
EP0900334B1 EP98902953A EP98902953A EP0900334B1 EP 0900334 B1 EP0900334 B1 EP 0900334B1 EP 98902953 A EP98902953 A EP 98902953A EP 98902953 A EP98902953 A EP 98902953A EP 0900334 B1 EP0900334 B1 EP 0900334B1
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EP
European Patent Office
Prior art keywords
valve
pressure
fuel
closing member
spring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP98902953A
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German (de)
French (fr)
Other versions
EP0900334A1 (en
Inventor
Wolfgang Fehlmann
Ruben-Sebastian Henning
Walter Fuchs
Stephan Jonas
Kiyotaka Ogata
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
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Robert Bosch GmbH
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Publication date
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Publication of EP0900334A1 publication Critical patent/EP0900334A1/en
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Publication of EP0900334B1 publication Critical patent/EP0900334B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/462—Delivery valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7771—Bi-directional flow valves
    • Y10T137/7772—One head and seat carried by head of another
    • Y10T137/7774—Supporting valve spring carried by supporting valve

Definitions

  • the invention relates to a pressure valve of the type of claim 1.
  • a pressure valve of the type of claim 1. Such a thing from scripture DE 42 40 302 known pressure valve is in a delivery line between a pump workspace of a fuel injection pump and an injection point at the one to be supplied by this Internal combustion engine used.
  • the pressure valve has in a pipe socket forming a valve housing used valve body, which has an axial passage has and the with the pump workspace facing end face forms a first valve seat.
  • in the axial through channel of the valve body is an in Pressure valve closing element opening towards the injection point performed with the force of a first valve spring a sealing surface is held on the first valve seat.
  • there is an axial through hole in the pressure valve closing member arranged by a towards the pump work room opening backflow valve is closable.
  • the known pressure valve of the constant pressure valve design is that of the pump work room fuel flowing towards the injection point and the backflowing fuel is the first and the respectively Flow through the second valve spring radially from the outside inwards got to.
  • the gap between the two changes individual spring turns of the valve springs depending from the opening stroke of the respective valve member, so that when An undesired throttling effect flows through the valve springs occurs. This depends on the opening stroke of the The throttle effect that changes valve elements is impaired the flow behavior of the fuel at the pressure valve what affect the injection process at the injection valve Injection point can affect.
  • the pressure valve according to the invention with the characteristic Features of claim 1, however, has the Advantage that the pumped by the fuel injection pump Fuel does not flow radially through the valve springs, so that an unrestricted flow through the pressure valve is guaranteed is.
  • the fuel is used advantageously passed radially outside the valve springs, being between the radially outer peripheral surfaces of the valve springs and a housing wall surrounding each of them Fuel channel of large cross section is formed through the fuel can flow unthrottled.
  • the pressure valve closing element and the backflow valve axially one behind the other to arrange, the pressure valve closing member with its the End face facing the pump workspace at the same time second valve seat for the valve member of the backflow valve forms.
  • the opening stroke movements of the pressure valve closing member and the valve member of the backflow valve each advantageously by a stop piece limited, which at the same time the dead or damaged volume in Pressure valve reduced.
  • stop pieces on their the Valves facing away from recesses at their ends Circumferential surface that cross holes or cross openings with an axial blind hole in the valve member facing away End face are connected and with this blind hole connect each to the delivery line.
  • the second stop piece of the backflow valve in advantageously in the axial passage of the Valve body to be pressed in, being about the press-in depth the maximum opening stroke of the backflow valve can be adjusted.
  • the recesses or cuts on the Stop pieces, the spring plate of the backflow valve and Pressure valve closing member can be of all shapes have an unthrottled fuel flow simultaneous sufficient axial guidance of the components in the Allow valve body or in the valve housing.
  • the first stop of the pressure valve closing member prefferably be provided with an axial through hole, the injection-side part of the delivery line directly connects with the through hole in the pressure valve closing element, so that the fuel flowing back does not have a valve spring must flow through and unhindered to the backflow valve can overflow.
  • FIG. 1 shows this a longitudinal section through a first embodiment a pressure valve designed as a constant pressure valve which the fuel overflow on the second stop of the Backflow valve via cross bores
  • Figure 2 a second embodiment analogous to the representation of the figure 1, in which the fuel passage on the second stop the backflow valve via a bevel cut
  • Figure 3 shows a third embodiment analogous to the illustration of Figure 1, in which the passage of fuel on second stop piece via an oblique radial bore
  • Figure 4 shows a fourth embodiment analogous to the representation of Figure 1, in which in the first Stop piece of the pressure valve closing member has a through hole is provided.
  • Figure 1 shows a longitudinal section through a first Embodiment of the pressure valve 1 according to the invention, the one in a stepped through hole 3 Pipe socket forming valve housing 5 is used, the in turn in a housing, not shown, of a fuel injection pump is screwed in.
  • the pressure valve 1 is thereby in a conveyor line 7 between a part shown Pump working chamber 9 of the fuel injection pump and an injection point 11, in the form of an injection valve in the combustion chamber to be supplied, also not shown Internal combustion engine used, the through hole 3 in the valve housing 5 a part of this delivery line 7 forms.
  • the pressure valve 1 has a tubular Valve body 13 on the pump workspace in the Through hole 3 of the valve housing 5 is inserted.
  • the Valve body 13 has an axial through channel 15 and forms with its ring end face facing away from the pump work space a preferably conical first Valve seat surface 17.
  • This first valve seat surface 17 acts as a piston, partly in the axial passage 15 axially displaceably guided pressure valve closing member 19 together with a conical sealing surface 21.
  • the pressure valve closing member 19 is a first valve spring 23 held in contact with the first valve seat 17 and opens if the fuel pressure exceeds the closing force the first valve spring 23 in the direction of the injection point 11th
  • the pressure valve closing member 19 has an axial through hole 25 on that towards a pump work room 9 opening backflow valve 27 can be closed. there forms the annular end face facing the pump working space 9 of the pressure valve closing member 19 has a second valve seat surface 29 with which the valve member designed as ball 31 of the backflow valve 27 cooperates.
  • the valve ball 31 of the backflow valve 27 is by a second valve spring 33 via a spring plate 35 in contact with the second Valve seat 29 held, the second valve spring 33 on the other hand, stationary on a shoulder of the through-channel 15 is supported in the valve body 13.
  • a first stop 37 in one first valve spring 23 receiving enlarged in cross section Spring chamber 39 of the through bore 3 in the valve housing 5 is arranged.
  • the first stop piece 37 instructs its end facing away from the pressure valve closing member 19 Ring shoulder 41 on which the first valve spring 23 supports and so the first stop 37 against one Bore heel in the valve housing 5 delimiting the spring space 39 braced.
  • the first stop 37 also forms its end face facing the pressure valve closing member 19 a the lifting movement of the pressure valve closing member 19 delimiting stop surface, the first valve spring 23 encloses the first stop piece 37.
  • a second stop piece 43 is in the through channel 15 of the valve body 13 used that it with its Valve ball 31 facing away from the end face in contact with one Bore paragraph of the axial through channel 15 arrives and with its end face facing the valve ball 31 Stop face forms with a facing end face of the spring plate 35 interacts.
  • the second valve spring 33 is based on the same as for the first valve spring 23 Ring shoulder 45 of the second stop piece 43 and radially encloses that having the stop surface Part of the stop piece 43.
  • valve springs 23 and 33 are arranged so that between their outer circumferential surface and the wall of the Through hole 3 and the through channel 15 each Fuel channel is formed, unthrottled by the fuel from the pump work space 9 towards the injection point 11 can flow.
  • the second stop piece 43 has the Pump work space 9 facing a lower end face axial blind bore 47, which opens into the delivery line 7 and with radial transverse channels 49 (preferably grooves) the axial through channel 15 in the valve body 13 connected is.
  • The are in the area of the outlet openings Cross channels 49 also preferably three bevels 51 on second stop piece 43 provided one unthrottled fuel flow along the second Stop piece 43 with safe guidance of the Stop piece 43 in the axial through-channel 15 guarantee.
  • the spring plate 35 also preferably has 4 axially extending recesses 53 on its peripheral surface, the enable unimpeded passage of fuel.
  • the pressure valve closing member 19 has on his, on the Sealing surface 21 adjoining the through channel 15 of the Valve body 13 projecting end preferably three plane Grinds 55 on, which extend axially to the second valve seat 29 extend.
  • the first stop piece 37 has the same as the second Stop piece 43 on its injection point 11 facing End face a blind bore coaxial to the through hole 3 57 on the transverse channels 59 (preferably grooves) is connected to the spring chamber 39. Furthermore, that points first stop piece 37 in the area of the ring shoulder 41 to the Outlet openings of the transverse channels 59 preferably four planes Grindings for an unimpeded passage of fuel.
  • the pressure valve according to the invention works in the following Wise. Before the high-pressure delivery of the fuel injection pump begins there is a static pressure in the delivery line 7, in which the pressure valve 1 and the backflow valve 27 through the force of the first valve spring 23 and the second valve spring 33 are kept closed. Here is the preload the first valve spring 23 is larger than the biasing force of the second valve spring 33. With the start of High-pressure delivery at the fuel injection pump increases the pressure in the pump work space 9 above the opening pressure of the Pressure valve 1, so that the first valve seat 17 in the through channel 15 of the valve body 13 pending high fuel pressure the pressure valve closing member 19 against the restoring force the first valve spring 23 from the first valve seat 17 takes off.
  • the high pressure flows through it Fuel the second stop piece 43 via the Openings 47, 49, 51 continue to flow along the recesses 53 of the spring plate 35 and the pressure valve closing member 19 into the spring chamber 39 and from there via the openings 59, 57 on the first stop piece 37 further into the through hole 3 in the valve housing 5 and from there into the delivery line 7 Injection point 11.
  • This is where the high fuel pressure comes in known manner on the fuel injector Injection into the internal combustion engine to be supplied.
  • the fuel flows through the pressure valve 1 and the backflow valve 27 along the fuel passages radially outward of the valve springs 23, 33 so that the Fuel unthrottled through the constant pressure valve Injection point 11 can flow.
  • the spring preload can be the valve springs 23 and 33 on the training the thickness of the ring shoulder on the stop pieces 37 and 43 to adjust.
  • the second embodiment shown in Figure 2 of the pressure valve according to the invention differs first embodiment only in the training of second stop piece 43 of the return valve 27.
  • Das second connector 43 has instead of the simple Blind bore a contour bore 63 in its the ball valve member 31 facing away from the end face, which is inclined trained flat grinding 65 on the peripheral wall of the cylindrical second stop piece 43 with the axial Through channel 15 in the valve body 13 is connected.
  • Fuel flow geometry the advantage that the Flow resistance is very low and at the same time one sufficient contact area on the valve body 13 and for the second valve spring 33 is guaranteed.
  • the third embodiment of the Pressure valve according to the invention differs in that Figure 1 illustrated first embodiment only in the formation of the second stop piece 43.
  • the second Stop piece 43 is in Figure 3 with his in Cross section enlarged circumferential surface on its the ball valve member 31 facing away into the wall of the through-channel 15 pressed into the valve body 13.
  • the fuel flow now takes place on the second stop piece 43 via radial oblique bores 67 which are axial Surface grinding 69 on the peripheral surface of the second Stop piece 43 starting in the axial blind bore 47 in the end of the second stop piece facing away from the valve member 43 flow out.
  • the fourth embodiment shown in Figure 4 differs from that shown in FIG. 1 first embodiment in the design of the first stop piece 37 of the pressure valve 1 and second stop piece 43 of the backflow valve 27 now has the first stop 37 instead of one Blind bore an axial through bore 71, from which in in a known manner, preferably lead away four transverse channels 59.
  • the transverse channels 59 open in the area of the ring shoulder 41 on the peripheral wall of the first stop piece 47 which in this area has flat cuts.
  • the Passage of fuel in the direction of flow to the injection point 11 continues from the spring chamber 39 via the transverse channels 59 and the bore 71 in the through bore 3 and further the delivery line 7. This flow takes place especially when the pressure valve closing member is in contact with the stop piece 37 19.
  • the second stop piece 43 is like the sectional view the stop piece 43 removable, now with a Provided a plurality of radial oblique bores 67 which in an axial blind bore 47 open.
  • the outlet openings the oblique holes 67 in the through channel 15 are there on an inclined shoulder 73 of the second stop piece 43 provided, which once again has an advantageous effect on the flow behavior of fuel through the second stop 43 affects because the fuel flow is not strong is redirected.
  • the fourth embodiment has the special one Advantage that the fuel flow both towards Injection point 11 back as well as in the opposite direction the pump working space 9 never one of the valve springs 23, 33 must flow through.

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Druckventil nach der Gattung des Patentanspruchs 1 aus. Ein derartiges aus der Schrift DE 42 40 302 bekanntes Druckventil ist in eine Förderleitung zwischen einem Pumpenarbeitsraum einer Kraftstoffeinspritzpumpe und einer Einspritzstelle an der von dieser zu versorgenden Brennkraftmaschine eingesetzt. Dabei weist das Druckventil einen in einen ein Ventilgehäuse bildenden Rohrstutzen eingesetzten Ventilkörper auf, der einen axialen Durchgangskanal aufweist und der mit seiner dem Pumpenarbeitsraum abgewandten Stirnfläche einen ersten Ventilsitz bildet. Im axialen Durchgangskanal des Ventilkörpers ist ein in Richtung Einspritzstelle öffnendes Druckventilschließglied geführt, das durch die Kraft einer ersten Ventilfeder mit einer Dichtfläche am ersten Ventilsitz gehalten wird. Dabei ist im Druckventilschließglied eine axiale Durchgangsbohrung angeordnet, die von einem in Richtung Pumpenarbeitsraum öffnenden Rückströmventil verschließbar ist. Während des Betriebs der Kraftstoffeinspritzpumpe wird durch ein unter hohem Druck stehendes Medium, das dem Druckventil aus dem Pumpenarbeitsraum über die Förderleitung zugeführt wird, das Druckventilschließglied gegen die Kraft der ersten Ventilfeder vom ersten Ventilsitz abgehoben, wodurch das Druckventil in Richtung Einspritzstelle öffnet. Am Ende der Hochdruckförderung kehrt das Druckventilschließglied auf seinen Ventilsitz zurück. Zugleich schließt ein Einspritzventil an der Einspritzstelle, wodurch in dem eingeschlossenen Volumen zwischen Druckventil und Einspritzventil Druckwellen hinund herlaufen die in der Lage sind, das Einspritzventil nochmals zu öffnen. Um dies zu vermeiden öffnet nunmehr das im Druckventilschließglied angeordnete Rückströmventil, über das sich das Druckniveau in der Förderleitung auch nach dem Schließen des Druckventilschließgliedes auf einen Standdruck abbauen kann, der durch die Vorspannung der zweiten Ventilfeder des Rückströmventils einstellbar ist.The invention relates to a pressure valve of the type of claim 1. Such a thing from Scripture DE 42 40 302 known pressure valve is in a delivery line between a pump workspace of a fuel injection pump and an injection point at the one to be supplied by this Internal combustion engine used. The pressure valve has in a pipe socket forming a valve housing used valve body, which has an axial passage has and the with the pump workspace facing end face forms a first valve seat. in the axial through channel of the valve body is an in Pressure valve closing element opening towards the injection point performed with the force of a first valve spring a sealing surface is held on the first valve seat. there is an axial through hole in the pressure valve closing member arranged by a towards the pump work room opening backflow valve is closable. During the Operation of the fuel injection pump is controlled by an under high pressure medium, which the pressure valve from the Pump workspace is supplied via the delivery line, the Pressure valve closing element against the force of the first valve spring lifted off the first valve seat, causing the pressure valve opens towards the injection point. At the end of high pressure production the pressure valve closing member returns to its Valve seat back. At the same time, an injection valve connects the injection point, creating in the enclosed volume between pressure valve and injection valve pressure waves are able to run the injector to open again. To avoid this, open the now backflow valve arranged in the pressure valve closing member, via that the pressure level in the delivery line also changes after Closing the pressure valve closing member to a standing pressure can break down by the bias of the second Valve spring of the backflow valve is adjustable.

Dabei weist das bekannte Druckventil der Gleichdruckventilbauweise jedoch den Nachteil auf, daß der vom Pumpenarbeitsraum in Richtung Einspritzstelle strömende Kraftstoff und der rückströmende Kraftstoff jeweils die erste bzw. die zweite Ventilfeder radial von außen nach innen durchströmen muß. Dabei verändert sich jedoch das Spaltmaß zwischen den einzelnen Federwindungen der Ventilfedern in Abhängigkeit vom Öffnungshub des jeweiligen Ventilgliedes, so daß beim Durchströmen der Ventilfedern ein ungewollter Drosseleffekt auftritt. Dieser sich in Abhängigkeit vom Öffnungshub der Ventilglieder verändernde Drosseleffekt beeinträchtigt dabei das Durchströmverhalten des Kraftstoffes am Druckventil, was sich negativ auf den Einspritzverlauf am Einspritzventil der Einspritzstelle auswirken kann.The known pressure valve of the constant pressure valve design However, the disadvantage is that of the pump work room fuel flowing towards the injection point and the backflowing fuel is the first and the respectively Flow through the second valve spring radially from the outside inwards got to. However, the gap between the two changes individual spring turns of the valve springs depending from the opening stroke of the respective valve member, so that when An undesired throttling effect flows through the valve springs occurs. This depends on the opening stroke of the The throttle effect that changes valve elements is impaired the flow behavior of the fuel at the pressure valve what affect the injection process at the injection valve Injection point can affect.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Druckventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß der von der Kraftstoffeinspritzpumpe geförderte Kraftstoff die Ventilfedern nicht radial durchströmt, so daß ein ungedrosseltes Durchströmen des Druckventils gewährleistet ist. Dabei wird der Kraftstoff in vorteilhafter Weise radial außerhalb der Ventilfedern an diesen vorbeigeleitet, wobei zwischen den radial äußeren Umfangsflächen der Ventilfedern und einer diese jeweils umgebenden Gehäusewand ein Kraftstoffkanal großen Querschnittes gebildet ist, durch den der Kraftstoff ungedrosselt durchströmen kann.The pressure valve according to the invention with the characteristic Features of claim 1, however, has the Advantage that the pumped by the fuel injection pump Fuel does not flow radially through the valve springs, so that an unrestricted flow through the pressure valve is guaranteed is. The fuel is used advantageously passed radially outside the valve springs, being between the radially outer peripheral surfaces of the valve springs and a housing wall surrounding each of them Fuel channel of large cross section is formed through the fuel can flow unthrottled.

Dabei ist es besonderes vorteilhaft das Druckventilschließglied und das Rückströmventil axial hintereinanderliegend anzuordnen, wobei das Druckventilschließglied mit seiner dem Pumpenarbeitsraum zugewandten Stirnfläche gleichzeitig einen zweiten Ventilsitz für das Ventilglied des Rückströmventils bildet. Die Öffnungshubbewegungen des Druckventilschließgliedes und des Ventilgliedes des Rückströmventils werden dabei in vorteilhafter Weise jeweils durch ein Anschlagstück begrenzt, das gleichzeitig das Tot- bzw. Schadvolumen im Druckventil reduziert. Für einen ungehinderten Kraftstoffdurchtritt weisen diese Anschlagstücke dabei an ihren den Ventilgliedern abgewandten Enden Ausnehmungen an ihrer Umfangfläche auf, die über Querbohrungen bzw. Queröffnungen mit einer axialen Sackbohrung in der ventilgliedabgewandten Stirnfläche verbunden sind und die mit dieser Sackbohrung jeweils an die Förderleitung anschließen. Des weiteren weisen auch der Federteller des Rückströmventils und der in den Ventilkörper ragende Teil des Druckventilschließgliedes axiale Ausnehmungen, vorzugsweise Anschliffe auf, die bei gleichzeitiger guter Führung der Bauteile im Ventilkörper einen ungedrosselten Kraftstoffdurchtritt ermöglichen. Dabei kann das zweite Anschlagstück des Rückströmventils in vorteilhafter Weise in den axialen Durchgangskanal des Ventilkörpers eingepreßt sein, wobei sich über die Einpreßtiefe der maximale Öffnungshubweg des Rückströmventils einstellen läßt. Die Ausnehmungen bzw. Anschliffe an den Anschlagstücken, dem Federteller des Rückströmventils und am Druckventilschließglied können dabei sämtliche Formen aufweisen, die einen ungedrosselten Kraftstoffdurchtritt bei gleichzeitiger ausreichender axialer Führung der Bauteile im Ventilkörper bzw. im Ventilgehäuse ermöglichen. Alternativ ist es möglich das erste Anschlagstück des Druckventilschließgliedes mit einer axialen Durchgangsbohrung zu versehen, die den einspritzseitigen Teil der Förderleitung direkt mit der Durchgangsbohrung im Druckventilschließglied verbindet, so daß auch der rückströmende Kraftstoff keine Ventilfeder durchströmen muß und ungehindert zum Rückströmventil überströmen kann.It is particularly advantageous for the pressure valve closing element and the backflow valve axially one behind the other to arrange, the pressure valve closing member with its the End face facing the pump workspace at the same time second valve seat for the valve member of the backflow valve forms. The opening stroke movements of the pressure valve closing member and the valve member of the backflow valve each advantageously by a stop piece limited, which at the same time the dead or damaged volume in Pressure valve reduced. For an unimpeded passage of fuel have these stop pieces on their the Valves facing away from recesses at their ends Circumferential surface that cross holes or cross openings with an axial blind hole in the valve member facing away End face are connected and with this blind hole connect each to the delivery line. Furthermore also have the spring plate of the backflow valve and the in the valve body projecting part of the pressure valve closing member axial recesses, preferably bevels on the at simultaneous good guidance of the components in the valve body allow unthrottled fuel passage. there can the second stop piece of the backflow valve in advantageously in the axial passage of the Valve body to be pressed in, being about the press-in depth the maximum opening stroke of the backflow valve can be adjusted. The recesses or cuts on the Stop pieces, the spring plate of the backflow valve and Pressure valve closing member can be of all shapes have an unthrottled fuel flow simultaneous sufficient axial guidance of the components in the Allow valve body or in the valve housing. alternative it is possible the first stop of the pressure valve closing member to be provided with an axial through hole, the the injection-side part of the delivery line directly connects with the through hole in the pressure valve closing element, so that the fuel flowing back does not have a valve spring must flow through and unhindered to the backflow valve can overflow.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Zeichnung, der Beschreibung und den Patentansprüchen entnehmbar.Further advantages and advantageous configurations of the object the invention are the drawing, the description and the patent claims.

Zeichnungdrawing

Vier Ausführungsbeispiele des erfindungsgemäßen Druckventils sind in der Zeichnung dargestellt und werden in der nachfolgenden Beschreibung näher erläutert. Es zeigen die Figur 1 einen Längsschnitt durch ein erstes Ausführungsbeispiel eines als Gleichdruckventil ausgebildeten Druckventils bei dem der Kraftstoffübertritt am zweiten Anschlagstück des Rückströmventils über Querbohrungen erfolgt, die Figur 2 ein zweites Ausführungsbeispiel analog zur Darstellung der Figur 1, bei dem der Kraftstoffdurchtritt am zweiten Anschlagstück des Rückströmventils über einen Schräganschliff erfolgt, die Figur 3 ein drittes Ausführungsbeispiel analog zur Darstellung der Figur 1, bei dem der Kraftstoffdurchtritt am zweiten Anschlagstück über eine schräge Radialbohrung erfolgt und die Figur 4 ein viertes Ausführungsbeispiel analog zur Darstellung der Figur 1, bei dem im ersten Anschlagstück des Druckventilschließgliedes eine Durchgangsbohrung vorgesehen ist.Four embodiments of the pressure valve according to the invention are shown in the drawing and are shown in the following Description explained in more detail. FIG. 1 shows this a longitudinal section through a first embodiment a pressure valve designed as a constant pressure valve which the fuel overflow on the second stop of the Backflow valve via cross bores, Figure 2 a second embodiment analogous to the representation of the figure 1, in which the fuel passage on the second stop the backflow valve via a bevel cut, which Figure 3 shows a third embodiment analogous to the illustration of Figure 1, in which the passage of fuel on second stop piece via an oblique radial bore and Figure 4 shows a fourth embodiment analogous to the representation of Figure 1, in which in the first Stop piece of the pressure valve closing member has a through hole is provided.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Die Figur 1 zeigt einen Längsschnitt durch ein erstes Ausführungsbeispiel des erfindungsgemäßen Druckventils 1, das in eine gestufte Durchgangsbohrung 3 eines einen Rohrstutzen bildenden Ventilgehäuses 5 eingesetzt ist, das seinerseits in ein nicht dargestelltes Gehäuse einer Kraftstoffeinspritzpumpe eingeschraubt ist. Das Druckventil 1 ist dabei in eine Förderleitung 7 zwischen einem zum Teil dargestellten Pumpenarbeitsraum 9 der Kraftstoffeinspritzpumpe und einer Einspritzstelle 11, in Form eines Einspritzventils in den Brennraum der zu versorgenden, ebenfalls nicht dargestellten Brennkraftmaschine eingesetzt, wobei die Durchgangsbohrung 3 im Ventilgehäuse 5 einen Teil dieser Förderleitung 7 bildet. Das Druckventil 1 weist einen rohrförmigen Ventilkörper 13 auf, der pumpenarbeitsraumseitig in die Durchgangsbohrung 3 des Ventilgehäuses 5 eingesetzt ist. Der Ventilkörper 13 weist dabei einen axialen Durchgangskanal 15 auf und bildet mit seiner pumpenarbeitsraumabgewandten Ringstirnfläche eine vorzugsweise konisch ausgebildete erste Ventilsitzfläche 17. Mit dieser ersten Ventilsitzfläche 17 wirkt ein kolbenförmiges, zum Teil im axialen Durchgangskanal 15 axial verschiebbar geführtes Druckventilschließglied 19 mit einer konischen Dichtfläche 21 zusammen. Das Druckventilschließglied 19 wird dabei von einer ersten Ventilfeder 23 in Anlage am ersten Ventilsitz 17 gehalten und öffnet bei Überschreiten des Kraftstoffdruckes über die Schließkraft der ersten Ventilfeder 23 in Richtung Einspritzstelle 11.Figure 1 shows a longitudinal section through a first Embodiment of the pressure valve 1 according to the invention, the one in a stepped through hole 3 Pipe socket forming valve housing 5 is used, the in turn in a housing, not shown, of a fuel injection pump is screwed in. The pressure valve 1 is thereby in a conveyor line 7 between a part shown Pump working chamber 9 of the fuel injection pump and an injection point 11, in the form of an injection valve in the combustion chamber to be supplied, also not shown Internal combustion engine used, the through hole 3 in the valve housing 5 a part of this delivery line 7 forms. The pressure valve 1 has a tubular Valve body 13 on the pump workspace in the Through hole 3 of the valve housing 5 is inserted. The Valve body 13 has an axial through channel 15 and forms with its ring end face facing away from the pump work space a preferably conical first Valve seat surface 17. With this first valve seat surface 17 acts as a piston, partly in the axial passage 15 axially displaceably guided pressure valve closing member 19 together with a conical sealing surface 21. The pressure valve closing member 19 is a first valve spring 23 held in contact with the first valve seat 17 and opens if the fuel pressure exceeds the closing force the first valve spring 23 in the direction of the injection point 11th

Das Druckventilschließglied 19 weist eine axiale Durchgangsbohrung 25 auf, die von einem in Richtung Pumpenarbeitsraum 9 öffnenden Rückströmventil 27 verschließbar ist. Dabei bildet die dem Pumpenarbeitsraum 9 zugewandte Ringstirnfläche des Druckventilschließgliedes 19 eine zweite Ventilsitzfläche 29 mit der das als Kugel 31 ausgebildete Ventilglied des Rückströmventils 27 zusammenwirkt. Die Ventilkugel 31 des Rückströmventils 27 wird dabei von einer zweiten Ventilfeder 33 über einen Federteller 35 in Anlage am zweiten Ventilsitz 29 gehalten, wobei sich die zweite Ventilfeder 33 andererseits ortsfest an einem Absatz des Durchgangskanals 15 im Ventilkörper 13 abstützt. Zur Begrenzung der Öffnungshubbewegungen des Druckventilschließgliedes 19 und der Ventilkugel 31 sind weiterhin zwei Anschlagstücke vorgesehen, von denen ein erstes Anschlagstück 37 in einen die erste Ventilfeder 23 aufnehmenden im Querschnitt erweiterten Federraum 39 der Durchgangsbohrung 3 im Ventilgehäuse 5 angeordnet ist. Das erste Anschlagstück 37 weist dabei an seinem dem Druckventilschließglied 19 abgewandten Ende einen Ringabsatz 41 auf, an dem sich die erste Ventilfeder 23 abstützt und so das erste Anschlagstück 37 gegen einen den Federraum 39 begrenzenden Bohrungsabsatz im Ventilgehäuse 5 verspannt. Dabei bildet das erste Anschlagstück 37 mit seiner dem Druckventilschließglied 19 zugewandten Stirnfläche eine die Hubbewegung des Druckventilschließgliedes 19 begrenzende Anschlagfläche, wobei die erste Ventilfeder 23 das erste Anschlagstück 37 umschließt.The pressure valve closing member 19 has an axial through hole 25 on that towards a pump work room 9 opening backflow valve 27 can be closed. there forms the annular end face facing the pump working space 9 of the pressure valve closing member 19 has a second valve seat surface 29 with which the valve member designed as ball 31 of the backflow valve 27 cooperates. The valve ball 31 of the backflow valve 27 is by a second valve spring 33 via a spring plate 35 in contact with the second Valve seat 29 held, the second valve spring 33 on the other hand, stationary on a shoulder of the through-channel 15 is supported in the valve body 13. To limit the opening stroke movements of the pressure valve closing member 19 and Valve ball 31 two stop pieces are also provided, of which a first stop 37 in one first valve spring 23 receiving enlarged in cross section Spring chamber 39 of the through bore 3 in the valve housing 5 is arranged. The first stop piece 37 instructs its end facing away from the pressure valve closing member 19 Ring shoulder 41 on which the first valve spring 23 supports and so the first stop 37 against one Bore heel in the valve housing 5 delimiting the spring space 39 braced. The first stop 37 also forms its end face facing the pressure valve closing member 19 a the lifting movement of the pressure valve closing member 19 delimiting stop surface, the first valve spring 23 encloses the first stop piece 37.

Ein zweites Anschlagstück 43 ist so in den Durchgangskanal 15 des Ventilkörpers 13 eingesetzt, daß es mit seiner der Ventilkugel 31 abgewandten Stirnfläche in Anlage an einen Bohrungsabsatz des axialen Durchgangskanals 15 gelangt und mit seiner der Ventilkugel 31 zugewandten Stirnfläche eine Anschlagfläche bildet die mit einer zugewandten Stirnfläche des Federtellers 35 zusammenwirkt. Die zweite Ventilfeder 33 stützt sich analog zur ersten Ventilfeder 23 an einem Ringabsatz 45 des zweiten Anschlagstückes 43 ab und umschließt dabei radial den die Anschlagfläche aufweisenden Teil des Anschlagstückes 43.A second stop piece 43 is in the through channel 15 of the valve body 13 used that it with its Valve ball 31 facing away from the end face in contact with one Bore paragraph of the axial through channel 15 arrives and with its end face facing the valve ball 31 Stop face forms with a facing end face of the spring plate 35 interacts. The second valve spring 33 is based on the same as for the first valve spring 23 Ring shoulder 45 of the second stop piece 43 and radially encloses that having the stop surface Part of the stop piece 43.

Dabei sind die Ventilfedern 23 und 33 so angeordnet, daß zwischen ihren äußeren Umfangsmantelflächen und der Wand der Durchgangsbohrung 3 bzw. des Durchgangskanals 15 jeweils ein Kraftstoffkanal gebildet ist, durch den Kraftstoff ungedrosselt vom Pumpenarbeitsraum 9 in Richtung Einspritzstelle 11 strömen kann.The valve springs 23 and 33 are arranged so that between their outer circumferential surface and the wall of the Through hole 3 and the through channel 15 each Fuel channel is formed, unthrottled by the fuel from the pump work space 9 towards the injection point 11 can flow.

Um einen ungedrosselten Kraftstoffdurchtritt am Druckventil 1 und Rückströmventil 27 zu gewährleisten weisen die Anschlagstücke 37 und 43 sowie der Federteller 35 und das Druckventilschließglied 19 an seinem in den Durchgangskanal 15 ragenden Ende die in den vergrößerten Schnittdarstellungen gezeigten Ausnehmungen bzw. Bohrungen auf, die nunmehr in Strömungsrichtung zur Einspritzstelle 11 hin nacheinander genauer beschrieben werden.For unrestricted fuel passage at the pressure valve 1 and backflow valve 27 to ensure the Stop pieces 37 and 43 and the spring plate 35 and that Pressure valve closing member 19 at its in the through channel 15 protruding end in the enlarged sectional views shown recesses or holes, which now in the flow direction to the injection point 11 one after the other be described in more detail.

Das zweite Anschlagstück 43 weist dabei an seiner dem Pumpenarbeitsraum 9 zugewandten unteren Stirnfläche eine axiale Sackbohrung 47 auf, die in die Förderleitung 7 mündet und die über radiale Querkanäle 49( vorzugsweise Nuten) mit dem axialen Durchgangskanal 15 im Ventilkörper 13 verbunden ist. Dabei sind im Bereich der Austrittsöffnungen der Querkanäle 49 zudem vorzugsweise drei Anschliffe 51 am zweiten Anschlagstück 43 vorgesehen, die einen ungedrosselten Kraftstoffdurchtritt entlang des zweiten Anschlagstückes 43 bei gleichzeitiger sicherer Führung des Anschlagstückes 43 im axialen Durchgangskanal 15 gewährleisten.The second stop piece 43 has the Pump work space 9 facing a lower end face axial blind bore 47, which opens into the delivery line 7 and with radial transverse channels 49 (preferably grooves) the axial through channel 15 in the valve body 13 connected is. The are in the area of the outlet openings Cross channels 49 also preferably three bevels 51 on second stop piece 43 provided one unthrottled fuel flow along the second Stop piece 43 with safe guidance of the Stop piece 43 in the axial through-channel 15 guarantee.

Der Federteller 35 weist ebenfalls vorzugsweise 4 axial verlaufende Ausnehmungen 53 an seiner Umfangsfläche auf, die einen ungehinderten Kraftstoffdurchtritt ermöglichen. The spring plate 35 also preferably has 4 axially extending recesses 53 on its peripheral surface, the enable unimpeded passage of fuel.

Das Druckventilschließglied 19 weist an seinem, an die Dichtfläche 21 anschließenden in den Durchgangskanal 15 des Ventilkörpers 13 ragenden Ende vorzugsweise drei plane Anschliffe 55 auf, die sich axial bis an die zweite Ventilsitzfläche 29 erstrecken.The pressure valve closing member 19 has on his, on the Sealing surface 21 adjoining the through channel 15 of the Valve body 13 projecting end preferably three plane Grinds 55 on, which extend axially to the second valve seat 29 extend.

Das erste Anschlagstück 37 weist analog zum zweiten Anschlagstück 43 an seiner der Einspritzstelle 11 zugewandten Stirnfläche eine zur Durchgangsbohrung 3 koaxiale Sackbohrung 57 auf, die über Querkanäle 59 (vorzugsweise Nuten) mit dem Federraum 39 verbunden ist. Darüberhinaus weist das erste Anschlagstück 37 im Bereich des Ringabsatzes 41 an den Austrittsöffnungen der Querkanäle 59 vorzugsweise vier plane Anschliffe für einen ungehinderten Kraftstoffdurchtritt auf.The first stop piece 37 has the same as the second Stop piece 43 on its injection point 11 facing End face a blind bore coaxial to the through hole 3 57 on the transverse channels 59 (preferably grooves) is connected to the spring chamber 39. Furthermore, that points first stop piece 37 in the area of the ring shoulder 41 to the Outlet openings of the transverse channels 59 preferably four planes Grindings for an unimpeded passage of fuel.

Das erfindungsgemäße Druckventil arbeitet in folgender Weise. Vor Beginn der Hochdruckförderung der Kraftstoffeinspritzpumpe herrscht in der Förderleitung 7 ein Standdruck, bei dem das Druckventil 1 und das Rückströmventil 27 durch die Kraft der ersten Ventilfeder 23 und der zweiten Ventilfeder 33 verschlossen gehalten werden. Dabei ist die Vorspannkraft der ersten Ventilfeder 23 größer ausgebildet als die Vorspannkraft der zweiten Ventilfeder 33. Mit Beginn der Hochdruckförderung an der Kraftstoffeinspritzpumpe steigt der Druck im Pumpenarbeitsraum 9 über den Öffnungsdruck des Druckventils 1, so daß der am ersten Ventilsitz 17 im Durchgangskanal 15 des Ventilkörpers 13 anstehende Kraftstoffhochdruck das Druckventilschließglied 19 entgegen der Rückstellkraft der ersten Ventilfeder 23 vom ersten Ventilsitz 17 abhebt. Dabei durchströmt der unter hohem Druck stehende Kraftstoff zunächst das zweite Anschlagstück 43 über die Öffnungen 47, 49, 51, strömt weiter entlang der Ausnehmungen 53 des Federtellers 35 und des Druckventilschließgliedes 19 in den Federraum 39 und von dort über die Öffnungen 59, 57 am ersten Anschlagstück 37 weiter in die Durchgangsbohrung 3 im Ventilgehäuse 5 und von dort in die Förderleitung 7 zur Einspritzstelle 11. Dort gelangt der Kraftstoffhochdruck in bekannter Weise am Kraftstoffeinspritzventil zur Einspritzung in die zu versorgende Brennkraftmaschine. Dabei erfolgt die Kraftstoffdurchströmung durch das Druckventil 1 und das Rückströmventil 27 entlang der Kraftstoffkanäle radial auswärts der Ventilfedern 23, 33, so daß der Kraftstoff ungedrosselt durch das Gleichdruckventil zur Einspritzstelle 11 strömen kann.The pressure valve according to the invention works in the following Wise. Before the high-pressure delivery of the fuel injection pump begins there is a static pressure in the delivery line 7, in which the pressure valve 1 and the backflow valve 27 through the force of the first valve spring 23 and the second valve spring 33 are kept closed. Here is the preload the first valve spring 23 is larger than the biasing force of the second valve spring 33. With the start of High-pressure delivery at the fuel injection pump increases the pressure in the pump work space 9 above the opening pressure of the Pressure valve 1, so that the first valve seat 17 in the through channel 15 of the valve body 13 pending high fuel pressure the pressure valve closing member 19 against the restoring force the first valve spring 23 from the first valve seat 17 takes off. The high pressure flows through it Fuel the second stop piece 43 via the Openings 47, 49, 51 continue to flow along the recesses 53 of the spring plate 35 and the pressure valve closing member 19 into the spring chamber 39 and from there via the openings 59, 57 on the first stop piece 37 further into the through hole 3 in the valve housing 5 and from there into the delivery line 7 Injection point 11. This is where the high fuel pressure comes in known manner on the fuel injector Injection into the internal combustion engine to be supplied. there the fuel flows through the pressure valve 1 and the backflow valve 27 along the fuel passages radially outward of the valve springs 23, 33 so that the Fuel unthrottled through the constant pressure valve Injection point 11 can flow.

Nach Beendigung der Hochdruckförderung im Pumpenarbeitsraum 9 sinkt der Druck in der Förderleitung 7 sehr rasch wieder unter den notwendigen Öffnungsdruck des Druckventils 1, so daß die erste Ventilfeder 23 das Druckventilschließglied 19 erneut in Anlage an den ersten Ventilsitz 17 zurück bewegt. Die durch das Verschließen des Einspritzventils 11 und des Druckventils 1 in der Förderleitung 7 entstehende Kraftstoffdruckwelle entspannt sich dabei über das Rückströmventil 27, wozu der in der Durchgangsbohrung 25 im Druckventilschließglied 19 anstehende Kraftstoffdruck das Kugelventilglied 31 entgegen der Rückstellkraft der zweiten Ventilfeder 33 vom zweiten Ventilsitz 29 abhebt. Dabei strömt nunmehr der Kraftstoff aus der Förderleitung 7 über den Federraum 39 durch die Durchgangsbohrung 25 im Druckventilschließglied 19 in den Durchgangskanal 15 im Ventilkörper 13 und über das zweite Anschlagstück 43 zurück in den Pumpenarbeitsraum 9. Nach Erreichen eines einstellbaren Standdrucks in der Förderleitung 7 übersteigt die Kraft der zweiten Ventilfeder 33 erneut den verbleibenden Kraftstoffdruck in der Förderleitung 7 und drückt so das Kugelventilglied 31 erneut in eine dichtende Anlage an den zweiten Ventilsitz 29. Die Öffnungshubbewegungen der Ventilglieder 19 und 31 sind dabei durch Anlage an den Anschlagstücken 37 und 43 begrenzt. Desweiteren läßt sich die Federvorspannkraft der Ventilfedern 23 und 33 über die Ausbildung der Dicke des Ringabsatzes an den Anschlagstücken 37 und 43 einstellen.After the high-pressure delivery in the pump work room has ended 9, the pressure in the delivery line 7 drops again very quickly under the necessary opening pressure of the pressure valve 1, so that the first valve spring 23, the pressure valve closing member 19th moved back into contact with the first valve seat 17. The by closing the injector 11 and the Pressure valve 1 arising in the delivery line 7 Fuel pressure wave relaxes over the Backflow valve 27, for which in the through hole 25 in Pressure valve closing member 19 pending fuel pressure Ball valve member 31 against the restoring force of the second Valve spring 33 lifts off the second valve seat 29. there the fuel now flows out of the delivery line 7 the spring chamber 39 through the through hole 25 in the pressure valve closing member 19 in the passage 15 in the valve body 13 and via the second stop piece 43 back into the Pump work room 9. After reaching an adjustable one Stand pressure in the delivery line 7 exceeds the force of second valve spring 33 again the remaining fuel pressure in the delivery line 7 and so presses the ball valve member 31 again in a sealing system on the second Valve seat 29. The opening stroke movements of the valve members 19 and 31 are by abutment on the stop pieces 37 and 43 limited. Furthermore, the spring preload can be the valve springs 23 and 33 on the training the thickness of the ring shoulder on the stop pieces 37 and 43 to adjust.

Das in der Figur 2 dargestellte zweite Ausführungsbeispiel des erfindungsgemäßen Druckventils unterscheidet sich zum ersten Ausführungsbeispiel lediglich in der Ausbildung des zweiten Anschlagstückes 43 des Rückströmventils 27. Das zweite Anschlußstück 43 weist dabei anstelle der einfachen Sackbohrung eine Konturbohrung 63 in seiner dem Kugelventilglied 31 abgewandten Stirnfläche auf, die über schräg ausgebildete Flachanschliffe 65 an der Umfangswand des zylinderförmigen zweiten Anschlagstückes 43 mit dem axialen Durchgangskanal 15 im Ventilkörper 13 verbunden ist. Dabei hat diese in der Figur 2 auch in einer Schnittdarstellung durch das zweite Anschlagstück 43 dargestellte Kraftstoffdurchströmgeometrie den Vorteil, daß der Strömungswiderstand sehr gering ist und gleichzeitig eine ausreichende Auflagefläche am Ventilkörper 13 und für die zweite Ventilfeder 33 gewährleistet ist.The second embodiment shown in Figure 2 of the pressure valve according to the invention differs first embodiment only in the training of second stop piece 43 of the return valve 27. Das second connector 43 has instead of the simple Blind bore a contour bore 63 in its the ball valve member 31 facing away from the end face, which is inclined trained flat grinding 65 on the peripheral wall of the cylindrical second stop piece 43 with the axial Through channel 15 in the valve body 13 is connected. there has this in Figure 2 in a sectional view represented by the second stop piece 43 Fuel flow geometry the advantage that the Flow resistance is very low and at the same time one sufficient contact area on the valve body 13 and for the second valve spring 33 is guaranteed.

Das in der Figur 3 gezeigte dritte Ausführungsbeispiel des erfindungsgemäßen Druckventils unterscheidet sich zum in der Figur 1 dargestellten ersten Ausführungsbeispiel lediglich in der Ausbildung des zweiten Anschlagstückes 43. Das zweite Anschlagstück 43 ist dabei bei der Figur 3 mit seiner im Querschnitt vergrößerten Umfangsfläche an seiner dem Kugelventilglied 31 abgewandten Seite in die Wand des Durchgangskanals 15 im Ventilkörper 13 eingepresst. Die Kraftstoffdurchströmung am zweiten Anschlagstück 43 erfolgt nunmehr über radiale Schrägbohrungen 67, die von axialen Flächenanschliffen 69 an der Umfangsfläche des zweiten Anschlagstücks 43 ausgehend in die axiale Sackbohrung 47 in der ventilgliedabgewandten Stirnseite des zweiten Anschlagstückes 43 münden. The third embodiment of the Pressure valve according to the invention differs in that Figure 1 illustrated first embodiment only in the formation of the second stop piece 43. The second Stop piece 43 is in Figure 3 with his in Cross section enlarged circumferential surface on its the ball valve member 31 facing away into the wall of the through-channel 15 pressed into the valve body 13. The fuel flow now takes place on the second stop piece 43 via radial oblique bores 67 which are axial Surface grinding 69 on the peripheral surface of the second Stop piece 43 starting in the axial blind bore 47 in the end of the second stop piece facing away from the valve member 43 flow out.

Das in der Figur 4 dargestellte vierte Ausführungsbeispiel unterscheidet sich gegenüber dem in der Figur 1 dargestellten ersten Ausführungsbeispiel in der konstruktiven Ausführung des ersten Anschlagstücks 37 des Druckventils 1 und des zweiten Anschlagstücks 43 des Rückströmventils 27. Dabei weist das erste Anschlagstück 37 nunmehr anstelle einer Sackbohrung eine axiale Durchgangsbohrung 71 auf, von der in bekannter Weise vorzugsweise vier Querkanäle 59 abführen. Die Querkanäle 59 münden dabei im Bereich des Ringabsatzes 41 an die Umfangswand des ersten Anschlagstücks 47 die in diesem Bereich flache Anschliffe aufweist. Dabei erfolgt der Kraftstoffdurchtritt in Strömungsrichtung zur Einspritzstelle 11 hin weiterhin aus dem Federraum 39 über die Querkanäle 59 und die Bohrung 71 in die Durchgangsbohrung 3 und weiter die Förderleitung 7. Diese Durchströmung erfolgt insbesondere bei am Anschlagstück 37 anliegendem Druckventilschließglied 19. Die Kraftstoffströmung in Gegenrichtung von der Einspritzstelle 11 in den Pumpenarbeitsraum 9 erfolgt jedoch nunmehr über die Durchgangsbohrung 71 im ersten Anschlagstück 37, von wo aus der Kraftstoff ungedrosselt in die dazu koaxiale Durchgangsbohrung 25 im Druckventilschließglied 19 bis an den zweiten Ventilsitz 29 weiterströmen kann. Diese Ausbildung hat dabei den Vorteil, daß sich die rückströmende Kraftstoffmenge sehr rasch und ungedrosselt und ohne Umlenkung bis an das Rückströmventil 27 fortsetzen kann.The fourth embodiment shown in Figure 4 differs from that shown in FIG. 1 first embodiment in the design of the first stop piece 37 of the pressure valve 1 and second stop piece 43 of the backflow valve 27 now has the first stop 37 instead of one Blind bore an axial through bore 71, from which in in a known manner, preferably lead away four transverse channels 59. The transverse channels 59 open in the area of the ring shoulder 41 on the peripheral wall of the first stop piece 47 which in this area has flat cuts. The Passage of fuel in the direction of flow to the injection point 11 continues from the spring chamber 39 via the transverse channels 59 and the bore 71 in the through bore 3 and further the delivery line 7. This flow takes place especially when the pressure valve closing member is in contact with the stop piece 37 19. The fuel flow in the opposite direction from the injection point 11 into the pump work space 9 now takes place via the through hole 71 in the first stop 37, from where the fuel unthrottled in the coaxial through bore 25 in Pressure valve closing member 19 up to the second valve seat 29 can continue to flow. This training has the advantage that the amount of fuel flowing back very quickly and unthrottled and without deflection up to the backflow valve 27 can continue.

Das zweite Anschlagstück 43 ist wie auch der Schnittdarstellung des Anschlagstücks 43 entnehmbar, nunmehr mit einer Vielzahl von radialen Schrägbohrungen 67 versehen, die in eine axiale Sackbohrung 47 münden. Die Austrittsöffnungen der Schrägbohrungen 67 in den Durchgangskanal 15 sind dabei an einer schrägen Schulter 73 des zweiten Anschlagstücks 43 vorgesehen, was sich noch einmal vorteilhaft auf das Durchströmverhalten des Kraftstoffes durch das zweite Anschlagstück 43 auswirkt, da die Kraftstoffströmung nicht stark umgelenkt wird.The second stop piece 43 is like the sectional view the stop piece 43 removable, now with a Provided a plurality of radial oblique bores 67 which in an axial blind bore 47 open. The outlet openings the oblique holes 67 in the through channel 15 are there on an inclined shoulder 73 of the second stop piece 43 provided, which once again has an advantageous effect on the flow behavior of fuel through the second stop 43 affects because the fuel flow is not strong is redirected.

Dabei hat das vierte Ausführungsbeispiel den besonderen Vorteil, daß die Kraftstoffströmung sowohl in Richtung zur Einspritzstelle 11 hin als auch in Gegenrichtung zurück in den Pumpenarbeitsraum 9 niemals eine der Ventilfedern 23, 33 durchströmen muß.The fourth embodiment has the special one Advantage that the fuel flow both towards Injection point 11 back as well as in the opposite direction the pump working space 9 never one of the valve springs 23, 33 must flow through.

Claims (2)

  1. Pressure valve for incorporation into a feed line (7) between a pump working space (9) of a fuel injection pump and an injection point (11) on the internal combustion engine to be supplied, with a valve body (13) having a first valve seat (17) and having an axial passage duct (15), in which is guided a pressure-valve closing member (19) which opens towards the injection point (11) counter to the force of a first valve spring (23) and which has a sealing face (21) co-operating with the first valve seat (17), and with, in the pressure-valve closing member (19), an axial passage bore (25) which can be closed by means of a non-return valve (27) opening in the direction of the pump working space (9) and having a second valve spring (33), there being formed between the radially outer circumferential faces of the first and second valve springs (23, 33) and a housing wall surrounding the latter a fuel duct through which the fuel flows, unthrottled, from the pump working space (9) in the direction of the injection point (11), characterized in that, with the pressure-valve closing member open for the connection between the pump working space and the injection point, stop pieces (37, 43) for the pressure-valve closing member and for the non-return valve member have at their ends facing away from the valve members (19, 31), on their circumferential face, recesses which are connected via connecting ducts (49, 59) to a central recess (47, 57) in the end faces facing away from the valve members, part of the feed line (7) issuing in each case onto the said end faces, in that axial recesses (53) are provided on the circumferential face of a spring plate (35) of the non-return valve (27), and in that the pressure-valve closing member (19) has at least one axial ground-down portion (55) on its circumferential face adjoining the sealing face (21) and projecting into the valve body (13).
  2. Pressure valve according to Claim 1, characterized in that the second stop piece (43) is pressed with part of its circumferential face into the passage duct (15) of the valve body (13).
EP98902953A 1997-03-15 1998-01-12 Pressure valve Expired - Lifetime EP0900334B1 (en)

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DE19710891 1997-03-15
DE19710891A DE19710891A1 (en) 1997-03-15 1997-03-15 Pressure valve
PCT/DE1998/000084 WO1998041755A1 (en) 1997-03-15 1998-01-12 Pressure valve

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EP0900334A1 EP0900334A1 (en) 1999-03-10
EP0900334B1 true EP0900334B1 (en) 2003-08-27

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EP0900334A1 (en) 1999-03-10
DE59809397D1 (en) 2003-10-02
WO1998041755A1 (en) 1998-09-24
US6196201B1 (en) 2001-03-06
DE19710891A1 (en) 1998-09-17
JP2000511264A (en) 2000-08-29

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