EP2399030B1 - Device for restricting the throughflow quantity at a pump, and pump arrangement having a device of this type - Google Patents

Device for restricting the throughflow quantity at a pump, and pump arrangement having a device of this type Download PDF

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Publication number
EP2399030B1
EP2399030B1 EP10702676.7A EP10702676A EP2399030B1 EP 2399030 B1 EP2399030 B1 EP 2399030B1 EP 10702676 A EP10702676 A EP 10702676A EP 2399030 B1 EP2399030 B1 EP 2399030B1
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EP
European Patent Office
Prior art keywords
throttle
pump
channel
spill
feed channel
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EP10702676.7A
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German (de)
French (fr)
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EP2399030A1 (en
Inventor
Christian Langenbach
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2399030A1 publication Critical patent/EP2399030A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/02—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid
    • F04F5/10—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid displacing liquids, e.g. containing solids, or liquids and elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/14—Combinations of two or more pumps the pumps being of different types at least one pump being of the non-positive-displacement type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing

Definitions

  • the invention relates to a device for limiting the flow rate to a pump, in particular to a suction-throttled feed pump, and to a pump arrangement with such a device.
  • the invention relates to the field of fuel injection systems of air compressing, self-igniting internal combustion engines.
  • a fuel injection system for an internal combustion engine has a pump and a delivery pump that delivers fuel to the pump.
  • the pump is a suction-throttled pump and is provided with a flow restrictor.
  • a Abberichtkanal which is connectable at its input side to an output of the pump and which opens at its outlet side at an opening point laterally into the inlet channel.
  • a throttle is arranged in the inlet channel, which can be configured as a cylindrical bore.
  • the throttle is designed such that with increasing Abschmenge flowing through the Ab tenual in the inlet channel, an increasing flow separation within the Throttle occurs, thereby reducing the effective throttle diameter and increases the throttle effect.
  • the cross section of the throttle is changed by the control device as a function of the discharge amount flowing via the discharge channel. This requires a large manufacturing cost of the pump and the flow rate limiting device.
  • the inventive device for flow rate limitation with the features of claim 1 and the pump assembly according to the invention with the features of claim 6 have the advantage that it is compact and can be produced with little effort.
  • the overflow valve configured as a pressure regulating valve controls a diversion amount through the diversion channel as a function of a pressure difference between the inlet side of the diversion channel and the outlet side of the diversion channel.
  • the throttle is oriented at least approximately on an axis of the inlet channel, along which the inlet channel extends at least between the outlet point and its outlet side. Furthermore, it is advantageous that an inlet of the throttle is arranged at least substantially in the region of the outlet point in the inlet channel.
  • the flow separation can increase advantageously with increasing Abberichtmenge which is introduced via the Ab jurykanal at the confluence point in the inlet channel.
  • Due to the arrangement of the throttle in the region of the discharge point a particularly effective influencing of the throttle coefficient via the crossflow from the discharge channel is possible.
  • a desired deterioration of the throttle coefficient can be achieved in a particularly effective manner.
  • the throttle may be arranged at a suitable distance close to the discharge point of the diversion channel.
  • a flow direction of the diversion channel at the outlet point is different from a flow direction of the inlet channel at the throttle.
  • the flow direction of the Abêtkanals at least approximately at the confluence with the flow direction of the inlet channel to the throttle includes an angle, said angle is in a range of about 40 ° to about 90 °.
  • a geometry optimization by a flow simulation calculation or the like is possible. This can be a particularly effective influence on the Main flow can be achieved by the cross flow.
  • the pump 3 is a part of the pump assembly 1, but no part of the device 2.
  • the device 2 for flow rate limitation and the pump assembly 1 with this device 2 can in particular for a Fuel injection system of air-compressing, self-igniting internal combustion engines are used.
  • the pump 3 is configured as a suction-throttled feed pump.
  • a preferred use of the pump assembly 1 and the device 2 is for a feed pump for supplying fuel to a high-pressure pump of a fuel injection system with a common rail that stores diesel fuel under high pressure.
  • the flow rate limiting device 2 according to the invention and the pump arrangement 1 according to the invention are also suitable for other applications.
  • the device 2 has an inlet channel 4 on the suction side of the pump 3, which has a throttle 5, and a discharge channel 6 also on the suction side of the pump 3, in which an overflow valve 7 is arranged, which is designed as a pressure control valve 7.
  • the inlet channel 4 is connected at its output side 8 to an inlet 9 of the pump 3.
  • the diversion channel 6 is connected at its input side 10 by means of a fuel line 11 to an outlet 12 of the pump 3.
  • the Abêtkanal 6 branches off from the fuel line, which leads, for example, to a high pressure pump of a fuel injection system.
  • the discharge channel 6 opens at its outlet side 13 at an outlet point 14 laterally into the inlet channel 4.
  • the throttle 5 is arranged between the discharge point 14 and the output side 8 of the inlet channel 4 in the inlet channel 4.
  • the inlet channel 4 has an axis 20.
  • the inlet channel 4 extends along the axis 20.
  • the inlet channel 4 extends between the outlet point 14 and its outlet side 8 along the axis 20.
  • the throttle 5 is aligned with the axis 20 of the inlet channel 4.
  • the throttle 5 is configured by a cylindrical bore.
  • a flow direction 21 of the inlet channel 4 on the throttle 5 is parallel to the axis 20 of the inlet channel 4.
  • the diversion channel 6 has an axis 22 on its output side 13.
  • a flow direction 23 of the diversion channel 6 at the point of discharge 14 is oriented parallel to the axis 22.
  • the axis 22 of the Abgreskanals 6 includes with the axis 20 of the inlet channel 4 at the discharge point 14 an angle 24 of about 90 °.
  • the flow direction 23 of the diversion channel 6 at the point of discharge 14 is different from the flow direction 21 of the inlet channel 4 at the throttle 5.
  • An inlet 25 of the throttle 5 is located in the region of the discharge point 14 in the inlet channel. 4
  • a flow 26 which is essentially determined by the main flow through the inlet channel 4. This results in an ideal throttle effect of the throttle 5.
  • the throttle coefficient is therefore optimal.
  • Fig. 2 shows the in Fig. 1 illustrated pump assembly 1 with the means 2 for limiting the flow rate at the pump 3 in a state in which a relatively large Abêtmenge is diverted via the Ab tenukanal 6 and is returned to the inlet channel 4.
  • the pressure control valve 7 controls the Abersonmenge through the Ab tenukanal 6 in response to a pressure difference between the input side 10 of the Abersonkanals 6 and the output side 13 of the Abêtkanals 6.
  • the pressure difference at the pressure control valve 7 is relatively large. This can be caused by a consumer downstream of the pump arrangement 1, in particular a high-pressure pump, requesting a relatively small amount of fuel. This results in the output 12 of the pump 3 to a relatively large pressure, which thus also prevails on the input side 10 of the Abersonkanals 6 and acts on the pressure control valve 7.
  • this causes the Abgresung a relatively large Abberichtmenge via the Ab tenukanal 6, which flows on the output side 13 as a cross-flow in the inlet channel 4. This cross flow is in the Fig. 2 schematically illustrated by a flow 27.
  • the diversion channel 6, in particular the outlet side 13 of the diversion channel 6, and the inlet channel 4, in particular the region of the inlet channel 4 at the outlet point 14, are designed so that hydraulic losses at the point of discharge 14 are avoided.
  • the over the Abêtkanal 6 of Main flow in the inlet channel 4 added transverse flow can thereby flow into the inlet channel 4 substantially lossless. Due to the superimposition of the crossflow to the main flow, there is a flow separation in the throttle 5.
  • the throttle 5 is designed so that with increasing cross flow, that is, with increasing Abêtmenge flowing through the Abjurikanal 6 in the inlet channel 4, an increasing flow separation occurs within the throttle 5. Due to the flow separation within the throttle 5 of the wall decreases the effective throttle diameter.
  • the throttle coefficient deteriorates, that is, the throttle effect of the throttle 5 increases.
  • the flow rate through the throttle 5 is reduced. This has a reducing effect on the pressure prevailing at the outlet 12 of the pump 3 and thus in the fuel line 11.
  • the pump assembly 1 can be used for a high-pressure pump of a fuel injection system with a common rail, the pump 3 as a mechanical prefeed pump, such as external gear pump used.
  • the pump 3 preferably operates largely in the suction-throttled operation in order to limit the delivery rate and thus the pressure which is established via the pressure regulating valve 7.
  • fuel can be conveyed out of a tank via the inlet channel 4, wherein the amount of diversion via the outlet channel 6 is likewise added to the inlet channel 4.
  • the flow direction 23 of the diversion channel 6 differs from the flow direction 21 of the inlet channel 4.
  • the two flow directions 21, 23 may enclose an angle from a range of about 40 ° to about 90 °.
  • the inlet via the inlet channel 4 is optimally carried out, since the throttle 5 is located on the axis 20 of the inlet channel 4 and is aligned with the axis 20.
  • the inlet from the diversion channel 6, takes place under a flow direction 23 swung out of the flow direction 21.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Einrichtung zur Durchflussmengenbegrenzung an einer Pumpe, insbesondere an einer sauggedrosselten Förderpumpe, und eine Pumpenanordnung mit solch einer Einrichtung. Speziell betrifft die Erfindung das Gebiet der Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen.The invention relates to a device for limiting the flow rate to a pump, in particular to a suction-throttled feed pump, and to a pump arrangement with such a device. Specifically, the invention relates to the field of fuel injection systems of air compressing, self-igniting internal combustion engines.

Aus der GB 1410 981 A ist eine Brennstoffeinspritzanlage für eine Brennkraftmaschine bekannt. Diese Brennstoffeinspritzanlage weist eine Pumpe und eine Förderpumpe auf, die Brennstoff zur Pumpe fördert. Die Pumpe ist eine sauggedrosselte Pumpe und für diese ist eine Einrichtung zur Durchflussmengenbegrenzung vorgesehen. Auf der Saugseite der Pumpe ist ein Zulaufkanal angeordnet, der an einer Ausgangsseite mit einem Eingang der Pumpe verbunden ist. Es ist ein Absteuerkanal vorgesehen, der an seiner Eingangsseite mit einem Ausgang der Pumpe verbindbar ist und der an seiner Ausgangsseite an einer Mündungsstelle seitlich in den Zulaufkanal mündet. In dem Absteuerkanal ist eine als Überströmventil wirkende Kontrolleinrichtung angeordnet und zwischen der Mündungsstelle und der Ausgangsseite des Zulaufkanals ist in dem Zulaufkanal eine Drossel angeordnet, die als zylinderförmige Bohrung ausgestaltet sein kann. Die Drossel ist derart ausgestaltet, dass mit zunehmender Absteuermenge, die über den Absteuerkanal in den Zulaufkanal strömt, eine zunehmende Strömungsablösung innerhalb der Drossel auftritt, wobei sich dadurch der wirksame Drosseldurchmesser verkleinert und die Drosselwirkung zunimmt. Zusätzlich wird der Querschnitt der Drossel durch die Kontrolleinrichtung abhängig von der über den Absteuerkanal strömenden Absteuermenge verändert. Dies erfordert einen großen Herstellungsaufwand der Pumpe und der Einrichtung zur Durchflussmengenbegrenzung.From the GB 1410 981 A a fuel injection system for an internal combustion engine is known. This fuel injection system has a pump and a delivery pump that delivers fuel to the pump. The pump is a suction-throttled pump and is provided with a flow restrictor. On the suction side of the pump, an inlet channel is arranged, which is connected at an output side to an input of the pump. It is provided a Absteuerkanal which is connectable at its input side to an output of the pump and which opens at its outlet side at an opening point laterally into the inlet channel. In the Absteuerkanal acting as overflow valve control device is arranged and between the orifice and the output side of the inlet channel, a throttle is arranged in the inlet channel, which can be configured as a cylindrical bore. The throttle is designed such that with increasing Absteuermenge flowing through the Absteuerkanal in the inlet channel, an increasing flow separation within the Throttle occurs, thereby reducing the effective throttle diameter and increases the throttle effect. In addition, the cross section of the throttle is changed by the control device as a function of the discharge amount flowing via the discharge channel. This requires a large manufacturing cost of the pump and the flow rate limiting device.

Durch die US 4 569 202 A ist ebenfalls eine Einrichtung zur Durchflussmengenbegrenzung an einer Pumpe bekannt. Bei dieser Einrichtung ist die Drossel als Drosselventil ausgebildet, das mit dem Überströmventil gekoppelt ist. Bei zunehmender Öffnung des Überströmventils und somit zunehmender Absteuermenge im Absteuerkanal wird das Drosselventil weiter geschlossen und somit der Querschnitt der Drossel verringert. Aufgrund des Drosselventils ist der Herstellungsaufwand der Pumpe und der Einrichtung zur Durchflussmengenbegrenzung auch bei dieser Ausführung groß.By the US 4,569,202A Also known is a device for limiting the flow rate to a pump. In this device, the throttle is designed as a throttle valve, which is coupled to the spill valve. With increasing opening of the overflow valve and thus increasing Absteuermenge in Absteuerkanal the throttle valve is further closed and thus reduces the cross-section of the throttle. Due to the throttle valve, the manufacturing cost of the pump and the flow rate limiting device is also large in this embodiment.

Offenbarung der ErfindungDisclosure of the invention

Die erfindungsgemäße Einrichtung zur Durchflussmengenbegrenzung mit den Merkmalen des Anspruchs 1 und die erfindungsgemäße Pumpenanordnung mit den Merkmalen des Anspruchs 6 haben den Vorteil, dass diese kompakt und mit geringem Aufwand herstellbar ist. Dabei ist es ferner vorteilhaft, dass das als Druckregelventil ausgestaltete Überströmventil eine Absteuermenge durch den Absteuerkanal in Abhängigkeit von einer Druckdifferenz zwischen der Eingangsseite des Absteuerkanals und der Ausgangsseite des Absteuerkanals steuert. Bei geringem Mengenbedarf und somit relativ hohem Druck kann somit eine Steigerung der Absteuermenge über den Absteuerkanal erzielt werden, was auf Grund der Zunahme der Querströmung zu einer Verschlechterung des Drosselbeiwerts führt. Somit reduziert sich die Durchflussmenge durch die Drossel und somit die Pumpe, was die gegebene Druckdifferenz reduziert. Dadurch kann eine vorteilhafte Durchflussmengenbegrenzung geschaffen werden, wobei die Lebensdauer und Verlustleistung optimiert sind.The inventive device for flow rate limitation with the features of claim 1 and the pump assembly according to the invention with the features of claim 6 have the advantage that it is compact and can be produced with little effort. In this case, it is further advantageous that the overflow valve configured as a pressure regulating valve controls a diversion amount through the diversion channel as a function of a pressure difference between the inlet side of the diversion channel and the outlet side of the diversion channel. With low volume requirements and thus relatively high pressure thus an increase in the Absteuermenge can be achieved via the diversion channel, which leads to a deterioration of the throttle coefficient due to the increase of the cross flow. Thus, the flow rate through the throttle and thus the pump reduces, which reduces the given pressure difference. As a result, an advantageous flow rate limitation can be created, with the service life and power loss being optimized.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen der im Anspruch 1 angegebenen Einrichtung und der im Anspruch 6 angegebenen Pumpenanordnung möglich.The measures listed in the dependent claims advantageous developments of the device specified in claim 1 and the pump arrangement specified in claim 6 are possible.

Vorteilhaft ist es, dass die Drossel zumindest näherungsweise an einer Achse des Zulaufkanals, entlang der sich der Zulaufkanal zumindest zwischen der Mündungsstelle und seiner Ausgangsseite erstreckt, ausgerichtet ist. Ferner ist es vorteilhaft, dass ein Eingang der Drossel zumindest im Wesentlichen im Bereich der Mündungsstelle in dem Zulaufkanal angeordnet ist. Durch die Ausrichtung der Drossel an der Achse des Zulaufkanals kann eine optimale Anströmung der Drossel von dem Zulaufkanal ermöglicht werden. Über den Absteuerkanal, der seitlich in den Zulaufkanal mündet, kann eine Querströmung erzeugt werden, wodurch eine gewollte Verschlechterung des Drosselbeiwerts der Drossel erzielt werden kann. Hierbei kann auf Grund der Querströmung eine Strömungsablösung innerhalb der Drossel erreicht werden. Die Strömungsablösung kann dabei in vorteilhafter Weise mit zunehmender Absteuermenge, die über den Absteuerkanal an der Mündungsstelle in den Zulaufkanal eingebracht wird, zunehmen. Durch die Anordnung der Drossel im Bereich der Mündungsstelle ist eine besonders wirksame Beeinflussung des Drosselbeiwerts über die Querströmung aus dem Absteuerkanal möglich. Bei dieser besonders wirksamen Beeinflussung des Drosselbeiwerts kann eine gewollte Verschlechterung des Drosselbeiwerts in besonders wirksamer Weise erzielt werden. Hierbei kann die Drossel in einem geeigneten Abstand nahe an der Mündungsstelle des Absteuerkanals angeordnet sein.It is advantageous that the throttle is oriented at least approximately on an axis of the inlet channel, along which the inlet channel extends at least between the outlet point and its outlet side. Furthermore, it is advantageous that an inlet of the throttle is arranged at least substantially in the region of the outlet point in the inlet channel. By aligning the throttle on the axis of the inlet channel, an optimal flow of the throttle from the inlet channel can be made possible. Via the diversion channel, which opens laterally into the inlet channel, a transverse flow can be generated, whereby a deliberate deterioration of the throttle coefficient of the throttle can be achieved. In this case, a flow separation within the throttle can be achieved due to the cross flow. The flow separation can increase advantageously with increasing Absteuermenge which is introduced via the Absteuerkanal at the confluence point in the inlet channel. Due to the arrangement of the throttle in the region of the discharge point, a particularly effective influencing of the throttle coefficient via the crossflow from the discharge channel is possible. In this particularly effective influencing of the throttle coefficient, a desired deterioration of the throttle coefficient can be achieved in a particularly effective manner. In this case, the throttle may be arranged at a suitable distance close to the discharge point of the diversion channel.

In vorteilhafter Weise ist eine Strömungsrichtung des Absteuerkanals an der Mündungsstelle unterschiedlich zu einer Strömungsrichtung des Zulaufkanals an der Drossel. Hierbei ist es ferner vorteilhaft, dass die Strömungsrichtung des Absteuerkanals an der Mündungsstelle mit der Strömungsrichtung des Zulaufkanals an der Drossel zumindest näherungsweise einen Winkel einschließt, wobei dieser Winkel in einem Bereich von etwa 40° bis etwa 90° liegt. Hierbei ist eine Geometrieoptimierung durch eine Strömungssimulationsrechnung oder dergleichen möglich. Dadurch kann eine besonders wirksame Beeinflussung der Hauptströmung durch die Querströmung erzielt werden.In an advantageous manner, a flow direction of the diversion channel at the outlet point is different from a flow direction of the inlet channel at the throttle. Here, it is also advantageous that the flow direction of the Absteuerkanals at least approximately at the confluence with the flow direction of the inlet channel to the throttle includes an angle, said angle is in a range of about 40 ° to about 90 °. Here, a geometry optimization by a flow simulation calculation or the like is possible. This can be a particularly effective influence on the Main flow can be achieved by the cross flow.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Bevorzugte Ausführungsbeispiele der Erfindung sind in der nachfolgenden Beschreibung anhand der beigefügten Zeichnungen, in denen sich entsprechende Elemente mit übereinstimmenden Bezugszeichen versehen sind, näher erläutert. Es zeigt:

  • Fig. 1 eine Pumpenanordnung mit einer Einrichtung zur Durchflussmengenbegrenzung in einer schematischen Darstellung entsprechend einem Ausführungsbeispiel der Erfindung in einem Zustand mit einer relativ geringen Absteuermenge und
  • Fig. 2 die in Fig. 1 dargestellte Pumpenanordnung mit der Einrichtung zur Durchflussmengenbegrenzung entsprechend dem Ausführungsbeispiel der Erfindung in einem Zustand mit einer relativ großen Absteuermenge.
Preferred embodiments of the invention are explained in more detail in the following description with reference to the accompanying drawings, in which corresponding elements are provided with corresponding reference numerals. It shows:
  • Fig. 1 a pump assembly with a device for flow rate limitation in a schematic representation according to an embodiment of the invention in a state with a relatively low Absteuermenge and
  • Fig. 2 in the Fig. 1 illustrated pump assembly with the device for flow rate limiting according to the embodiment of the invention in a state with a relatively large Absteuermenge.

Ausführungsformen der ErfindungEmbodiments of the invention

Fig. 1 zeigt eine Pumpenanordnung 1 mit einer Einrichtung 2 zur Durchflussmengenbegrenzung an einer Pumpe 3. Die Pumpe 3 ist dabei ein Teil der Pumpenanordnung 1, aber kein Teil der Einrichtung 2. Die Einrichtung 2 zur Durchflussmengenbegrenzung und die Pumpenanordnung 1 mit dieser Einrichtung 2 können insbesondere für eine Brennstoffeinspritzanlage von luftverdichtenden, selbstzündenden Brennkraftmaschinen dienen. Die Pumpe 3 ist dabei als sauggedrosselte Förderpumpe ausgestaltet. Ein bevorzugter Einsatz der Pumpenanordnung 1 und der Einrichtung 2 besteht für eine Förderpumpe zur Zuführung von Brennstoff zu einer Hochdruckpumpe einer Brennstoffeinspritzanlage mit einem Common-Rail, das Dieselbrennstoff unter hohem Druck speichert. Die erfindungsgemäße Einrichtung 2 zur Durchflussmengenbegrenzung und die erfindungsgemäße Pumpenanordnung 1 eignen sich jedoch auch für andere Anwendungsfälle. Fig. 1 The pump 3 is a part of the pump assembly 1, but no part of the device 2. The device 2 for flow rate limitation and the pump assembly 1 with this device 2 can in particular for a Fuel injection system of air-compressing, self-igniting internal combustion engines are used. The pump 3 is configured as a suction-throttled feed pump. A preferred use of the pump assembly 1 and the device 2 is for a feed pump for supplying fuel to a high-pressure pump of a fuel injection system with a common rail that stores diesel fuel under high pressure. However, the flow rate limiting device 2 according to the invention and the pump arrangement 1 according to the invention are also suitable for other applications.

Die Einrichtung 2 weist einen Zulaufkanal 4 auf der Saugseite der Pumpe 3, der eine Drossel 5 aufweist, und einen Absteuerkanal 6 ebenfalls auf der Saugseite der Pumpe 3 auf, in dem ein Überströmventil 7 angeordnet ist, das als Druckregelventil 7 ausgestaltet ist. Der Zulaufkanal 4 ist an seiner Ausgangsseite 8 mit einem Eingang 9 der Pumpe 3 verbunden. Der Absteuerkanal 6 ist an seiner Eingangsseite 10 mittels einer Brennstoffleitung 11 mit einem Ausgang 12 der Pumpe 3 verbunden. Der Absteuerkanal 6 zweigt dabei von der Brennstoffleitung ab, die beispielsweise zu einer Hochdruckpumpe einer Brennstoffeinspritzanlage führt. Der Absteuerkanal 6 mündet an seiner Ausgangsseite 13 an einer Mündungsstelle 14 seitlich in den Zulaufkanal 4. Die Drossel 5 ist zwischen der Mündungsstelle 14 und der Ausgangsseite 8 des Zulaufkanals 4 in dem Zulaufkanal 4 angeordnet.The device 2 has an inlet channel 4 on the suction side of the pump 3, which has a throttle 5, and a discharge channel 6 also on the suction side of the pump 3, in which an overflow valve 7 is arranged, which is designed as a pressure control valve 7. The inlet channel 4 is connected at its output side 8 to an inlet 9 of the pump 3. The diversion channel 6 is connected at its input side 10 by means of a fuel line 11 to an outlet 12 of the pump 3. The Absteuerkanal 6 branches off from the fuel line, which leads, for example, to a high pressure pump of a fuel injection system. The discharge channel 6 opens at its outlet side 13 at an outlet point 14 laterally into the inlet channel 4. The throttle 5 is arranged between the discharge point 14 and the output side 8 of the inlet channel 4 in the inlet channel 4.

Der Zulaufkanal 4 weist eine Achse 20 auf. Der Zulaufkanal 4 erstreckt sich entlang der Achse 20. Insbesondere erstreckt sich der Zulaufkanal 4 zwischen der Mündungsstelle 14 und seiner Ausgangsseite 8 entlang der Achse 20. Die Drossel 5 ist an der Achse 20 des Zulaufkanals 4 ausgerichtet. Dabei ist die Drossel 5 durch eine zylinderförmige Bohrung ausgestaltet. Dadurch ist eine Strömungsrichtung 21 des Zulaufkanals 4 an der Drossel 5 parallel zu der Achse 20 des Zulaufkanals 4.The inlet channel 4 has an axis 20. The inlet channel 4 extends along the axis 20. In particular, the inlet channel 4 extends between the outlet point 14 and its outlet side 8 along the axis 20. The throttle 5 is aligned with the axis 20 of the inlet channel 4. In this case, the throttle 5 is configured by a cylindrical bore. As a result, a flow direction 21 of the inlet channel 4 on the throttle 5 is parallel to the axis 20 of the inlet channel 4.

Der Absteuerkanal 6 weist an seiner Ausgangsseite 13 eine Achse 22 auf. Eine Strömungsrichtung 23 des Absteuerkanals 6 an der Mündungsstelle 14 ist parallel zu der Achse 22 orientiert. In diesem Ausführungsbeispiel schließt die Achse 22 des Absteuerkanals 6 mit der Achse 20 des Zulaufkanals 4 an der Mündungsstelle 14 einen Winkel 24 von etwa 90° ein. Die Strömungsrichtung 23 des Absteuerkanals 6 an der Mündungsstelle 14 ist dabei unterschiedlich zu der Strömungsrichtung 21 des Zulaufkanals 4 an der Drossel 5.The diversion channel 6 has an axis 22 on its output side 13. A flow direction 23 of the diversion channel 6 at the point of discharge 14 is oriented parallel to the axis 22. In this embodiment, the axis 22 of the Absteuerkanals 6 includes with the axis 20 of the inlet channel 4 at the discharge point 14 an angle 24 of about 90 °. The flow direction 23 of the diversion channel 6 at the point of discharge 14 is different from the flow direction 21 of the inlet channel 4 at the throttle 5.

Ein Eingang 25 der Drossel 5 liegt im Bereich der Mündungsstelle 14 in dem Zulaufkanal 4.An inlet 25 of the throttle 5 is located in the region of the discharge point 14 in the inlet channel. 4

Über den Zulaufkanal 4 strömt Brennstoff in einer Hauptströmungsrichtung zu der Drossel 5. Zu dieser Hauptströmung kommt eine Querströmung über den Absteuerkanal 6 in der Strömungsrichtung 23 hinzu, die von der über den Absteuerkanal 6 durch das Druckregelventil 7 abgesteuerten Brennstoffmenge abhängt. Dabei ist in der Fig. 1 eine Situation dargestellt, in der keine oder nur eine relativ kleine Absteuermenge auftritt. Somit ergibt sich in dem Zulaufkanal 4 vor dem Eingang 25 der Drossel 5 eine Strömung 26, die im Wesentlichen durch die Hauptströmung durch den Zulaufkanal 4 bestimmt ist. Hierdurch ergibt sich eine ideale Drosselwirkung der Drossel 5. Der Drosselbeiwert ist daher optimal.Fuel flows in a main flow direction to the throttle 5 via the inlet channel 4. A transverse flow via the outlet channel 6 in the flow direction 23, which depends on the amount of fuel removed via the outlet channel 6 by the pressure regulating valve 7, is added to this main flow. It is in the Fig. 1 presented a situation in which no or only a relatively small Absteuermenge occurs. Thus, in the inlet channel 4 in front of the inlet 25 of the throttle 5 there is a flow 26, which is essentially determined by the main flow through the inlet channel 4. This results in an ideal throttle effect of the throttle 5. The throttle coefficient is therefore optimal.

Fig. 2 zeigt die in Fig. 1 dargestellte Pumpenanordnung 1 mit der Einrichtung 2 zur Durchflussmengenbegrenzung an der Pumpe 3 in einem Zustand, in dem eine relativ große Absteuermenge über den Absteuerkanal 6 abgesteuert wird und in den Zulaufkanal 4 zurückgeführt wird. Fig. 2 shows the in Fig. 1 illustrated pump assembly 1 with the means 2 for limiting the flow rate at the pump 3 in a state in which a relatively large Absteuermenge is diverted via the Absteuerkanal 6 and is returned to the inlet channel 4.

Das Druckregelventil 7 steuert die Absteuermenge durch den Absteuerkanal 6 in Abhängigkeit von einer Druckdifferenz zwischen der Eingangsseite 10 des Absteuerkanals 6 und der Ausgangsseite 13 des Absteuerkanals 6. Bei der in der Fig. 2 dargestellten Situation ist die Druckdifferenz am Druckregelventil 7 relativ groß. Dies kann dadurch verursacht sein, dass ein der Pumpenanordnung 1 nachgeschalteter Verbraucher, insbesondere eine Hochdruckpumpe, eine relativ geringe Brennstoffmenge abfrägt. Hierdurch kommt es am Ausgang 12 der Pumpe 3 zu einem relativ großen Druck, der somit auch an der Eingangsseite 10 des Absteuerkanals 6 herrscht und auf das Druckregelventil 7 einwirkt. Dies bewirkt allerdings die Absteuerung einer relativ großen Absteuermenge über den Absteuerkanal 6, die an der Ausgangsseite 13 als Querströmung in den Zulaufkanal 4 einströmt. Diese Querströmung ist in der Fig. 2 schematisch durch einen Strömungsverlauf 27 veranschaulicht.The pressure control valve 7 controls the Absteuermenge through the Absteuerkanal 6 in response to a pressure difference between the input side 10 of the Absteuerkanals 6 and the output side 13 of the Absteuerkanals 6. In the in the Fig. 2 illustrated situation, the pressure difference at the pressure control valve 7 is relatively large. This can be caused by a consumer downstream of the pump arrangement 1, in particular a high-pressure pump, requesting a relatively small amount of fuel. This results in the output 12 of the pump 3 to a relatively large pressure, which thus also prevails on the input side 10 of the Absteuerkanals 6 and acts on the pressure control valve 7. However, this causes the Absteuerung a relatively large Absteuermenge via the Absteuerkanal 6, which flows on the output side 13 as a cross-flow in the inlet channel 4. This cross flow is in the Fig. 2 schematically illustrated by a flow 27.

Der Absteuerkanal 6, insbesondere die Ausgangsseite 13 des Absteuerkanals 6, und der Zulaufkanal 4, insbesondere der Bereich des Zulaufkanals 4 an der Mündungsstelle 14, sind so ausgestaltet, dass hydraulische Verluste an der Mündungsstelle 14 vermieden sind. Die über den Absteuerkanal 6 der Hauptströmung in dem Zulaufkanal 4 hinzugefügte Querströmung kann dadurch im Wesentlichen verlustfrei in den Zulaufkanal 4 einströmen. Durch die Überlagerung der Querströmung zur Hauptströmung kommt es zu einer Strömungsablösung in der Drossel 5. Dabei ist die Drossel 5 so ausgestaltet, dass mit zunehmender Querströmung, das heißt mit zunehmender Absteuermenge, die über den Absteuerkanal 6 in den Zulaufkanal 4 strömt, eine zunehmende Strömungsablösung innerhalb der Drossel 5 auftritt. Durch die Strömungsablösung innerhalb der Drossel 5 von der Wandung verkleinert sich der wirksame Drosseldurchmesser. Hierdurch verschlechtert sich der Drosselbeiwert, das heißt die Drosselwirkung der Drossel 5 nimmt zu. Somit reduziert sich bei gegebener Druckdifferenz die Durchflussmenge durch die Drossel 5. Dies wirkt sich reduzierend auf den am Ausgang 12 der Pumpe 3 und somit in der Brennstoffleitung 11 herrschenden Druck aus.The diversion channel 6, in particular the outlet side 13 of the diversion channel 6, and the inlet channel 4, in particular the region of the inlet channel 4 at the outlet point 14, are designed so that hydraulic losses at the point of discharge 14 are avoided. The over the Absteuerkanal 6 of Main flow in the inlet channel 4 added transverse flow can thereby flow into the inlet channel 4 substantially lossless. Due to the superimposition of the crossflow to the main flow, there is a flow separation in the throttle 5. The throttle 5 is designed so that with increasing cross flow, that is, with increasing Absteuermenge flowing through the Absteuerkanal 6 in the inlet channel 4, an increasing flow separation occurs within the throttle 5. Due to the flow separation within the throttle 5 of the wall decreases the effective throttle diameter. As a result, the throttle coefficient deteriorates, that is, the throttle effect of the throttle 5 increases. Thus, with a given pressure difference, the flow rate through the throttle 5 is reduced. This has a reducing effect on the pressure prevailing at the outlet 12 of the pump 3 and thus in the fuel line 11.

Beispielsweise kann die Pumpenanordnung 1 für eine Hochdruckpumpe einer Brennstoffeinspritzanlage mit einem Common-Rail dienen, wobei die Pumpe 3 als mechanische Vorförderpumpe, beispielsweise Außenzahnradpumpe, dient. Die Pumpe 3 arbeitet dabei vorzugsweise größtenteils im sauggedrosselten Betrieb, um die Fördermenge und damit den sich über das Druckregelventil 7 einstellenden Druck zu begrenzen. Über den Zulaufkanal 4 kann beispielsweise Brennstoff aus einem Tank gefördert werden, wobei die Absteuermenge über den Absteuerkanal 6 ebenfalls dem Zulaufkanal 4 hinzugefügt wird.For example, the pump assembly 1 can be used for a high-pressure pump of a fuel injection system with a common rail, the pump 3 as a mechanical prefeed pump, such as external gear pump used. The pump 3 preferably operates largely in the suction-throttled operation in order to limit the delivery rate and thus the pressure which is established via the pressure regulating valve 7. For example, fuel can be conveyed out of a tank via the inlet channel 4, wherein the amount of diversion via the outlet channel 6 is likewise added to the inlet channel 4.

Allerdings ergibt sich das Problem, das bei großem Einspritzmengenbedarf die Überschussmenge am Druckregelventil 7 klein wird und somit der Druck zur Füllung eines nachgeschalteten Verbrauchers, insbesondere eines Pumpenarbeitsraums, gering ist, während bei einem kleinen Einspritzmengenbedarf die Überschussmenge am Druckregelventil 7 groß wird, wodurch auch der Druck zur Füllung eines Verbrauchers, insbesondere eines Pumpenarbeitsraums ansteigt, obwohl in diesem Fall ein solcher Anstieg nicht erforderlich ist.However, there is the problem that at large injection quantity requirement, the excess amount at the pressure control valve 7 is small and thus the pressure for filling a downstream consumer, in particular a pump working space is low, while at a small injection quantity requirement, the excess amount at the pressure control valve 7 becomes large, whereby the Pressure for filling a consumer, in particular a pump working space increases, although in this case, such an increase is not required.

Bei der Pumpenanordnung 1 des Ausführungsbeispiels wird im Fall eines geringen Einspritzmengenbedarfs der Drosselbeiwert der als Saugdrossel dienenden Drossel 5 so verändert, dass die Drossel 5 einen größeren Widerstand darstellt, wodurch der Druckanstieg vor dem Druckregelventil 7 an der Pumpe 3 geringer ausfällt.In the pump assembly 1 of the embodiment, in the case of small injection quantity requirement of the throttle coefficient of the throttle serving as a suction throttle 5 changed so that the throttle 5 is a greater resistance, whereby the pressure increase upstream of the pressure control valve 7 to the pump 3 fails.

Dies wird durch eine seitliche Anströmung der Drossel 5 von der Strömung erreicht, bei der der Hauptströmung durch den Zulaufkanal 4 eine Querströmung aus dem Absteuerkanal 6 überlagert ist. Hierbei unterscheidet sich die Strömungsrichtung 23 des Absteuerkanals 6 von der Strömungsrichtung 21 des Zulaufkanals 4. Beispielsweise können die beiden Strömungsrichtungen 21, 23 einen Winkel aus einem Bereich von etwa 40° bis etwa 90° einschließen. Der Zulauf über den Zulaufkanal 4 erfolgt dabei optimal, da die Drossel 5 auf der Achse 20 des Zulaufkanals 4 liegt und an der Achse 20 ausgerichtet ist. Der Zulauf aus dem Absteuerkanal 6 erfolgt jedoch unter einer aus der Strömungsrichtung 21 herausgeschwenkten Strömungsrichtung 23.This is achieved by a lateral flow of the throttle 5 of the flow, in which the main flow is superimposed by the inlet channel 4, a cross flow from the Absteuerkanal 6. In this case, the flow direction 23 of the diversion channel 6 differs from the flow direction 21 of the inlet channel 4. For example, the two flow directions 21, 23 may enclose an angle from a range of about 40 ° to about 90 °. The inlet via the inlet channel 4 is optimally carried out, since the throttle 5 is located on the axis 20 of the inlet channel 4 and is aligned with the axis 20. The inlet from the diversion channel 6, however, takes place under a flow direction 23 swung out of the flow direction 21.

Im Fall einer knappen Mengenbilanzerfüllung, die eine Randbedingung darstellt und bei der eine minimale Absteuermenge am Druckregelventil 7 entsprechend der in Fig. 1 dargestellten Situation erreicht wird, strömt die größtmögliche Menge an Brennstoff durch die Drossel 5.In the case of a tight volume balance, which represents a boundary condition and in which a minimum amount of diversion at the pressure control valve 7 corresponding to the in Fig. 1 achieved situation, flows the largest possible amount of fuel through the throttle. 5

Im Fall einer ausreichenden Menge, bei der die Absteuermenge am Druckregelventil 7 nicht minimal ist, nimmt der Anteil der nicht optimal auf die Drossel 5 strömenden Menge, das heißt die Querströmung, zu, wodurch sich der Drosselbeiwert der Drossel 5 verschlechtert. Somit nimmt die insgesamt durch die Drossel 5 strömende Menge ab, bis sich ein Gleichgewichtszustand einstellt. Dieser Fall tritt beispielsweise bei höheren Zulaufdrücken zur Pumpe 3 oder bei einer geringen Mengenabnahme, beispielsweise im Schubbetrieb einer Brennkraftmaschine, auf.In the case of a sufficient amount in which the Absteuermenge at the pressure control valve 7 is not minimal, the proportion of not optimally flowing to the throttle 5 amount, that is, the cross-flow, increases, whereby the throttle coefficient of the throttle 5 deteriorates. Thus, the total amount flowing through the throttle 5 decreases until an equilibrium state is established. This case occurs, for example, at higher inlet pressures to the pump 3 or at a small decrease in volume, for example, in overrun operation of an internal combustion engine on.

Die verringerten Absteuermengen führen entsprechend der Kennlinie des Druckregelventils 7 zu einem verringerten Druck an allen beteiligten Komponenten und somit zu einer verringerten Verlustleistung und einer vergrößerten Lebensdauer. Ferner ergibt sich eine verringerte Absteuermengenvarianz und somit auch eine verringerte Druckvarianz. Hierbei kann bereits durch eine günstige Anordnung der Mündungsstelle 14 im Vorfeld der für die Drosselung zuständigen Drosselbohrung oder dergleichen, die die Drossel 5 bildet, eine vorteilhafte Wirkung erzielt werden, wodurch die Pumpenanordnung 1 kostengünstig ausgestaltet werden kann.The reduced Absteuermengen lead according to the characteristic of the pressure control valve 7 to a reduced pressure on all components involved and thus to a reduced power loss and an enlarged Lifespan. Furthermore, there is a reduced Absteuermengenvarianz and thus a reduced pressure variance. In this case, an advantageous effect can already be achieved by a favorable arrangement of the discharge point 14 in the run-up to the throttling bore responsible for the throttling or the like, which forms the throttle 5, whereby the pump arrangement 1 can be designed inexpensively.

Um eine vorteilhafte Anströmung der Drossel 5 über den Absteuerkanal 6 mit einer entsprechend großen Querströmung zu erzielen, sind Umlenkungen, Querschnittsverengungen und dergleichen innerhalb des Absteuerkanals 6 möglichst zu vermeiden.In order to achieve an advantageous flow against the throttle 5 via the diversion channel 6 with a correspondingly large cross flow, deflections, cross-sectional constrictions and the like within the Absteuerkanals 6 are to be avoided as possible.

Im Betrieb der Pumpenanordnung 1 können verschiedene Situationen auftreten, wobei zwei mögliche Situationen in den Fig. 1 und 2 veranschaulicht sind. Im Betrieb der Pumpenanordnung 1 führt der durch die Querströmung verschlechterte Drosselbeiwert der Drossel 5 zu einem verringerten Drosseldurchfluss durch die Drossel 5, wodurch sich wiederum die Absteuermenge durch den Absteuerkanal 6 über das Druckregelventil 7 so weit reduziert, bis sich ein Gleichgewicht zwischen beiden Effekten einstellt.In the operation of the pump assembly 1, various situations may occur, with two possible situations in the Fig. 1 and 2 are illustrated. During operation of the pump arrangement 1, the throttling coefficient of the throttle 5, which is impaired by the transverse flow, leads to a reduced throttle flow through the throttle 5, which in turn reduces the diversion amount through the bypass duct 6 via the pressure regulating valve 7 until an equilibrium is established between the two effects.

Claims (6)

  1. Device (2) for throughflow quantity limitation at a pump (3), in particular at a suction-throttled delivery pump for fuel injection of air-compressing, auto-ignition internal combustion engines, having a feed channel (4) on the suction side of the pump (3), which feed channel is at an outlet side (8) connected at least indirectly to an inlet (9) of the pump (3), having a spill channel (6), which at its inlet side (10) is connectable at least indirectly to an outlet (12) of the pump (3) and which at its output side (13) opens laterally into the feed channel (4) at a mouth point (14), having a flow transfer valve (7) arranged in the spill channel (6), and having a throttle (5) which is arranged in the feed channel (4) between the mouth point (14) and the outlet side (8) of the feed channel (4), wherein the throttle (5) is designed as a cylinder bore, and the throttle (5) is designed such that, with increasing spill quantity flowing via the spill channel (6) into the feed channel (4), increased flow separation arises within the throttle (5), wherein, as a result, the effective throttle diameter decreases and the throttling action increases, wherein the flow transfer valve (7) is in the form of a pressure regulating valve (7), characterized in that the pressure regulating valve (7) controls a spill quantity through the spill channel (6) in a manner dependent on a pressure difference between the inlet side (10) of the spill channel (6) and the outlet side (13) of the spill channel (6).
  2. Device for throughflow limitation according to Claim 1,
    characterized
    in that the throttle (5) is at least approximately aligned with an axis (20) of the feed channel (4) along which the feed channel (4) extends at least between the mouth point (14) and its outlet side (8).
  3. Device for throughflow limitation according to Claim 1 or 2,
    characterized
    in that an inlet (25) of the throttle (5) is arranged in the feed channel (4) at least substantially in the region of the mouth point (14).
  4. Device for throughflow quantity limitation according to any of Claims 1 to 3,
    characterized in that a flow direction (23) of the spill channel (6) at the mouth point (14) differs from a flow direction (21) of the feed channel (4) at the throttle (5) .
  5. Device for throughflow quantity limitation according to Claim 4,
    characterized
    in that the flow direction (23) of the spill channel (6) at the mouth point (14) at least approximately encloses an angle (24), which lies in a range from approximately 30° to approximately 100°, in particular in a range from approximately 40° to approximately 90°, with the flow direction (21) of the feed channel (4) at the throttle (5) .
  6. Pump arrangement (1), in particular for fuel injection systems of air-compressing, auto-ignition internal combustion engines, having a pump (3) and a device (2) for throughflow quantity limitation according to any of Claims 1 to 5, wherein the outlet side (8) of the feed channel (4) is connected at least indirectly to the inlet (9) of the pump (3), and wherein the inlet side (10) of the spill channel (6) is connected at least indirectly to the outlet (12) of the pump (3).
EP10702676.7A 2009-02-18 2010-02-04 Device for restricting the throughflow quantity at a pump, and pump arrangement having a device of this type Active EP2399030B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009000943A DE102009000943A1 (en) 2009-02-18 2009-02-18 Flow restriction device on a pump and pump assembly with such a device
PCT/EP2010/051359 WO2010094574A1 (en) 2009-02-18 2010-02-04 Device for restricting the throughflow quantity at a pump, and pump arrangement having a device of this type

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EP2399030A1 EP2399030A1 (en) 2011-12-28
EP2399030B1 true EP2399030B1 (en) 2019-06-05

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CN102325996B (en) 2016-02-03
EP2399030A1 (en) 2011-12-28
CN102325996A (en) 2012-01-18
WO2010094574A1 (en) 2010-08-26
DE102009000943A1 (en) 2010-08-19

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