EP0318714A2 - Exhaust gas recirculation device for internal combustion engines - Google Patents

Exhaust gas recirculation device for internal combustion engines Download PDF

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Publication number
EP0318714A2
EP0318714A2 EP19880118278 EP88118278A EP0318714A2 EP 0318714 A2 EP0318714 A2 EP 0318714A2 EP 19880118278 EP19880118278 EP 19880118278 EP 88118278 A EP88118278 A EP 88118278A EP 0318714 A2 EP0318714 A2 EP 0318714A2
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EP
European Patent Office
Prior art keywords
valve
control
exhaust gas
gas recirculation
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP19880118278
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German (de)
French (fr)
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EP0318714B1 (en
EP0318714A3 (en
Inventor
Klaus Dipl.-Ing. Krieger
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP0318714A3 publication Critical patent/EP0318714A3/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
    • F02M25/00—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture
    • F02M25/06—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture adding lubricant vapours
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages
    • F02M41/126—Variably-timed valves controlling fuel passages valves being mechanically or electrically adjustable sleeves slidably mounted on rotary piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/02—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered
    • F02D1/08—Transmission of control impulse to pump control, e.g. with power drive or power assistance
    • 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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/52—Systems for actuating EGR valves
    • F02M26/59—Systems for actuating EGR valves using positive pressure actuators; Check valves therefor
    • F02M26/62—Systems for actuating EGR valves using positive pressure actuators; Check valves therefor in response to fuel pressure
    • 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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/52—Systems for actuating EGR valves
    • F02M26/55—Systems for actuating EGR valves using vacuum actuators

Definitions

  • the invention relates to an exhaust gas recirculation device for internal combustion engines according to the preamble of the main claim.
  • a distributor injection pump serves as the fuel injection system, in which the start of delivery takes place via a speed-dependent hydraulic pressure prevailing in the pump suction chamber and at which this pressure is caused by a position of the sleeve of the aerodynamic speed regulator dependent drain opening is affected.
  • the position of the control sleeve is determined depending on the speed and load, since on the one hand the purely speed-dependent flying forces act on the control sleeve and in the opposite direction the forces which can be changed arbitrarily via the adjusting lever and which are entered by a control spring and correspond to the load.
  • the drain opening is reached by the control sleeve desired load and speed.
  • This type of control is very complex due to the use of a hydraulic pressure switch and a cam switch and is disadvantageous and also prone to failure due to the space requirement, quite apart from the fact that the throttle throttle has a certain cross-section, which causes the required switching pressure from a certain outflow quantity, but this does leads to the fact that with larger discharge quantities per time, i.e. at high speeds and open discharge opening, the throttle acts like a closure, so that the change in the pressure curve in the suction chamber intended for the adjustment of the start of delivery is suspended.
  • the exhaust gas recirculation device according to the invention with the characterizing features of the main claim has the advantage that the direct implementation of the hydraulic pressure for switching the directional control valve saves costs while reducing sources of interference.
  • a pressure-maintaining valve for the outflowing quantity is present parallel to the throttle throttle, via which the required actuating pressure of the servomotor of the directional control valve can be achieved.
  • An embodiment of the object of the invention is shown in the drawing and described in more detail below. It is a distributor injection pump in the Shown longitudinal section, which is used to control a schematically shown exhaust gas recirculation system.
  • a pump and distributor piston 1 is set in a reciprocating and simultaneously rotating movement by a drive shaft 2 and with the aid of a cam gear 3.
  • fuel is conveyed from a pump work chamber 4 via a longitudinal distribution groove 5 to one of a plurality of pressure channels 6, which are arranged around the pump and distributor piston 1 at uniform angular intervals and each lead to a combustion chamber (not shown) of an internal combustion engine.
  • the pump work chamber 4 is supplied with fuel via a suction channel 7 from a suction chamber 8 which is present in the housing of the injection pump and is filled with fuel, in that the suction channel 7 is opened during the suction stroke of the pump and distributor piston 1 by longitudinal control grooves 9 provided in the pump piston 1.
  • the number of control grooves 9 corresponds to the number of pressure channels 6 and thus the number of pressure strokes carried out with one revolution of the pump piston.
  • a solenoid valve 10 is arranged, which closes the suction channel 7 at the end of the injection, so that no fuel can get from the suction chamber 8 into the pump working chamber 4 during the suction stroke of the pump piston 1.
  • the quantity to be injected into the pressure channel 6 per stroke is determined by the axial position of a control slide 11 arranged around the pump piston 1. This axial position is determined by a speed controller 12 and an arbitrarily actuated adjusting lever 13, evaluating the respective speed and load (the load can correspond, for example, to the position of the accelerator pedal of the motor vehicle).
  • the suction chamber 8 is supplied with fuel by a feed pump 14, which is driven by the drive shaft 2 and supplies fuel from a fuel tank 15 and a suction line 16.
  • the output pressure of the feed pump 14 and thus the pressure in the suction chamber 8 is controlled by a pressure control valve 17, this pressure also increasing with increasing speed in accordance with a desired function.
  • the cam mechanism 3 and the speed controller 12 are arranged in the suction chamber 8 and are thus acted upon on all sides by this pressure and are lubricated by this fuel.
  • the cam drive 3, which is driven by the drive shaft 2, has a roller ring 19 which carries rollers 18 and which is rotatably mounted in the housing by a certain angle and in the U-shaped cross section of which the rollers 18 are mounted.
  • This roller ring 19 is coupled in a rotationally locking manner to an injection adjustment piston 22 via an adjustment bolt 21, this injection adjustment piston 22 being shown rotated by 90 ° in the drawing, ie actually perpendicular to the illustration level is adjustable.
  • this roller ring 19 there is a claw coupling in which the claws 23 on the output side of the drive shaft 2 mesh with the claws 24 on the drive side of the pumping and distributing piston 1, so that the pumping and distributing piston 1 independently of the drive shaft 2 exert a lifting movement while rotating can.
  • An end cam disk 25 is arranged on the pump piston 1 and runs with its end cam 26 on the rollers 18, the number of end cams in turn corresponding to the number of pressure channels 6.
  • the end cam disk 25 is pressed with its track onto the rollers 20 by springs 27, only one of which is shown.
  • the direction of displacement of the injection adjustment piston is chosen so that when the fuel pressure in the suction chamber 8 increases with increasing speed, the injection adjustment piston 22 is displaced counter to the return spring 28 and rotates the roller ring 19 so that the end cams 26 of the end cam disk 25 come into engagement with the rollers 18 earlier , whereby the start of the stroke of the pump piston 1 and thus the start of delivery of the fuel with respect to the rotational position of the drive shaft 2 is brought forward. So the higher the speed, the earlier the start of delivery (start of spraying).
  • the speed controller 12 is driven via a gear wheel 32 which is connected to the drive shaft 2 and drives a speed sensor 33 with flyweights 34 which, on the one hand, engage a control sleeve 35 which is axially displaceably mounted on an axis 36 and on the other hand by a control spring 37 attacks the control lever system 38, which links the control slide 11 for its stroke position.
  • the control lever system 38 is pivotally mounted on an axis 39 for this purpose.
  • the bias of the control spring 37 can be changed by the adjusting lever 13 in such a way that when the adjusting lever 13 is moved in the direction of increasing load, the bias of the control spring 37 also increases, so that the control slide 11 is pushed further up, which is due to a given later opening of a relief channel 41 of the pump work space 4 during the pressure stroke of the pump piston 1, an increase in the injection quantity results.
  • the control of the amount of fuel still in the pump working chamber 4 is always given when the orifices 42 of the relief channel 1 emerge from the control slide 11 during the pressure stroke of the pump piston 1 and the further fuel delivery of the pump piston 1 into the suction chamber 8 takes place.
  • the drain channel 44 is connected via a drain line 45 to the fuel tank 15, in which Drain line a pressure control valve 46 is arranged. Upstream of this pressure-maintaining valve 46, a hydraulic servomotor 47 of a pneumatic 3/2-way valve 48 is connected to the discharge line 45.
  • the directional control valve 48 controls a vacuum line 49, which leads from an exhaust gas recirculation valve 51 to a vacuum source 52.
  • the exhaust gas recirculation valve 51 which is loaded in the closing direction by a spring 53, is arranged in an exhaust gas recirculation line 54 of an engine 55, which is supplied with fuel via an injection line 56 from the pressure channel 6, which is delivered in the manner described above, with appropriate regulation of the quantity and the start of delivery .
  • the drain line 45 has a bypass 57 in which a throttling throttle 58 is arranged.
  • the exhaust gas recirculation control takes place in such a way that below a certain load at which the control bore 43 opens the drain channel 44, the fuel flowing there out of the suction chamber 8 and into the drain line 45 is stowed there by the throttling throttle 58 until the pressure control valve reaches a certain pressure 46 opens and allows the fuel to flow into the fuel tank 15 while maintaining this discharge pressure.
  • the pneumatic directional valve 48 is opened by the hydraulic servomotor 47, so that the exhaust gas recirculation valve 51 is opened by the vacuum source 52 against the force of the closing spring 53 via the vacuum line 49 and exhaust gas by the exhaust gas recirculation line 54 from the exhaust side of the engine can flow to the intake side.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)

Abstract

Exhaust gas recirculation device for internal combustion engines (55) with a fuel injection system, in which, in controlling the delivery start adjustment as a function of the load and engine speed on a specific load and speed characteristic curve, a hydraulic back- pressure builds up which serves directly for controlling a pneumatic directional valve (48) having a hydraulic servo motor (47), with which valve the exhaust gas return valve (51), functioning at a partial vacuum, is controlled and in which, in particular, the hydraulic back- pressure is controlled by means of a pressure-holding valve (46). …<IMAGE>…

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Abgasrückführeinrichtung für Brennkraftmaschinen nach der Gattung des Hauptan­spruchs.The invention relates to an exhaust gas recirculation device for internal combustion engines according to the preamble of the main claim.

Bekanntlich können die schädlichen Emissionen einer Brennkraftmaschine durch die Optimierung des Brennraumes und der Einspritzanlage nur bis zu einer bestimmten Grenze verringert werden. Die Kohlenwasserstoffemission wird durch die Spritzbeginnfrühverschiebung minimiert, wodurch die NOx-Emission ansteigt. Um diese NOx-Emission wieder zu reduzieren, wird bekanntlich die Abgasrück­führung vorgenommen, wofür verschiedene Methoden bekannt sind. Diese speziell für die Verringerung der Kohlen­wasserstoffemission durchgeführte Früherverstellung des Förderbeginns ist teilweise überlagert mit der ohnehin in der Einspritzanlage vorhandenen last- sowie drehzahlabhängigen Spritzbeginnregelung. Bekanntlich muß mit zunehmender Drehzahl der Förderbeginn auf früher verstellt werden, insbesondere um die natürliche Spritz­beginnspätverstellung mit zunehmender Drehzahl, die durch die winkelmäßig zunehmende Laufzeit der Druckwellen in der Einspritzleitung bedingt ist, auszugleichen. Eine Abgasrückführung darf nur unterhalb einer bestimmten Last erfolgen, d.h. unterhalb einer bestimmten Einspritz­menge, wobei sich dieser Wert mit der Drehzahl in etwa entsprechend den Lastkurven des Reglerkennfelds ändert.It is known that the harmful emissions of an internal combustion engine can only be reduced to a certain limit by optimizing the combustion chamber and the injection system. The hydrocarbon emission is minimized by the injection begin early shift, which increases NOx emissions. In order to reduce this NO x emission again, the exhaust gas recirculation is known to be carried out, for which various methods are known. This early adjustment of the start of delivery, which is carried out specifically for the reduction of hydrocarbon emissions, is partially superimposed on the load and load already present in the injection system speed-dependent spray start control. As is known, with increasing speed, the start of delivery must be adjusted to earlier, in particular in order to compensate for the natural late injection start with increasing speed, which is caused by the angularly increasing duration of the pressure waves in the injection line. Exhaust gas recirculation may only take place below a certain load, ie below a certain injection quantity, this value changing with the speed approximately in accordance with the load curves of the control map.

Bei einer bekannten Abgasrückführeinrichtung für Brenn­kraftmaschinen der gattungsgemäßen Art (DE-OS 29 46 557.4) dient als Kraftstoffeinspritzanlage eine Vertei­lereinspritzpumpe, bei der der Förderbeginn über einen im Pumpensaugraum herrschenden drehzahlabhängigen hydrau­lischen Druck erfolgt und bei der dieser Druck durch eine von der Lage der Muffe des Fliegkraftdrehzahlreglers abhängige Abflußöffnung beeinflußt wird. Die Lage der Regelmuffe ist drehzahl- und lastabhängig bestimmt, da einerseits an der Regelmuffe die rein drehzahlab­hängigen Fliegkräft angreifen und in entgegengesetzter Richtung die über den Verstellhebel willkürlich änderba­ren und durch eine Regelfeder eingegebenen der Last entsprechenden Kräfte. Die Abflußöffnung wird durch die Regelmuffe gewünschte Last und Drehzahl erreicht ist. Der durch die Abflußöffnung abströmende Kraftstoff wird durch eine Drossel gestaut, wobei dieser Staudruck auf einen Druckschalter in einer elektrischen Leitung des Magneten des Wegeventils wirkt. Außerdem ist in dieser elektrischen Leitung ein Schalter eingebaut, der über einen Schaltnocken des Verstellhebels, also für einen bestimmten Lastbereich, betätigt wird. Wenn beide Schalter geschlossen sind, schaltet das Wegeventil um, so daß das pneumatisch betätigte Abgasrückführventil geöffnet wird. Es handelt sich also nicht um eine stetige Regelung der Abgasrückführung, sondern um eine Auf-Zu­steuerung.In a known exhaust gas recirculation device for internal combustion engines of the generic type (DE-OS 29 46 557.4), a distributor injection pump serves as the fuel injection system, in which the start of delivery takes place via a speed-dependent hydraulic pressure prevailing in the pump suction chamber and at which this pressure is caused by a position of the sleeve of the aerodynamic speed regulator dependent drain opening is affected. The position of the control sleeve is determined depending on the speed and load, since on the one hand the purely speed-dependent flying forces act on the control sleeve and in the opposite direction the forces which can be changed arbitrarily via the adjusting lever and which are entered by a control spring and correspond to the load. The drain opening is reached by the control sleeve desired load and speed. The fuel flowing out through the discharge opening is blocked by a throttle, this dynamic pressure acting on a pressure switch in an electrical line of the magnet of the directional control valve. In addition, a switch is built into this electrical line, which is operated via a switch cam on the adjustment lever, i.e. for a specific load range. When both switches are closed, the directional control valve switches over so that the pneumatically operated exhaust gas recirculation valve is opened. So it is not a matter of a constant regulation of the exhaust gas recirculation, but of an open control.

Diese Art der Steuerung ist durch die Verwendung eines hydraulischen Druckschalters und eines Nockenschalters sehr aufwendig und aufgrund des Raumbedarfes nachteilig sowie auch störanfällig, ganz abgesehen davon, daß die Staudrossel einen bestimmten Querschnitt aufweist, der ab einer bestimmten Abströmmenge den erforderlichen Schaltdruck bewirkt, was jedoch dazu führt, daß bei größeren Abströmmengen pro Zeit, also bei hohen Drehzah­len und geöffneter Abflußöffnung, sich die Drossel wie ein Verschluß auswirkt, so daß die für die Anglei­chung des Förderbeginns vorgesehene Änderung des Druck­verlaufs im Saugraum aussetzt.This type of control is very complex due to the use of a hydraulic pressure switch and a cam switch and is disadvantageous and also prone to failure due to the space requirement, quite apart from the fact that the throttle throttle has a certain cross-section, which causes the required switching pressure from a certain outflow quantity, but this does leads to the fact that with larger discharge quantities per time, i.e. at high speeds and open discharge opening, the throttle acts like a closure, so that the change in the pressure curve in the suction chamber intended for the adjustment of the start of delivery is suspended.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Abgasrückführeinrichtung mit den kennzeichnenden Merkmalen des Hauptanspruchs hat dem­gegenüber den Vorteil, daß durch die direkte Umsetzung des hydraulischen Druckes zur Schaltung des Wegeventils Kosten gespart werden bei gleichzeitigem Vermindern von Störquellen.The exhaust gas recirculation device according to the invention with the characterizing features of the main claim has the advantage that the direct implementation of the hydraulic pressure for switching the directional control valve saves costs while reducing sources of interference.

Nach einer vorteilhaften Ausgestaltung der Erfindung bei Verwendung einer die im Oberbegriff des Anspruchs 4 angegebenen Merkmale aufweisenden Einspritzanlage ist parallel zur Staudrossel ein Druckhalteventil für die abströmende Menge vorhanden, über das der erforderli­che Stelldruck des Stellmotors des Wegeventils erzielbar ist.According to an advantageous embodiment of the invention when using an injection system having the features specified in the preamble of claim 4, a pressure-maintaining valve for the outflowing quantity is present parallel to the throttle throttle, via which the required actuating pressure of the servomotor of the directional control valve can be achieved.

Hierdurch wird vor allem erreicht, daß der Querschnitt der Staudrossel sehr eng gehalten werden kann, da die Staudrossel nun nur noch die Aufgabe hat, bei geschlos­sener Abflußöffnung an der Regelmuffe den hydraulischen Druck am hydraulischen Stellmotor so weit abzubauen, daß das Wegeventil wieder schließen kann. Das Druckhal­teventil hingegen hält bei abfließendem Kraftstoff gerade einen Druck aufrecht, wie er zum Betätigen des Stellmotors notwendig ist, der jedoch so gering ist, daß er keinen Einfluß auf den Druck im Saugraum hat, so daß die lastabhängige Förderbeginnsteuerung nicht beeinträchtigt ist.This primarily ensures that the cross-section of the damper can be kept very narrow, since the damper now only has the task of reducing the hydraulic pressure on the hydraulic servomotor with the drain opening closed so that the directional valve can close again. The pressure control valve, however, maintains a pressure when fuel is flowing away, as is necessary to actuate the servomotor, but is so small that it has no influence on the pressure in the suction chamber, so that the load-dependent delivery start control is not impaired.

Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Beschreibung, der Zeichnung und den Ansprüchen entnehmbar.Further advantages and advantageous embodiments of the invention can be found in the following description, the drawing and the claims.

Zeichnungdrawing

Ein Ausführungsbeispiel des Gegenstandes der Erfindung ist in der Zeichnung dargestellt und im folgenden näher beschrieben. Es ist eine Verteilereinspritzpumpe im Längsschnitt dargestellt, die zur Steuerung einer schema­tisch dargestellten Abgasrückführanlage dient.An embodiment of the object of the invention is shown in the drawing and described in more detail below. It is a distributor injection pump in the Shown longitudinal section, which is used to control a schematically shown exhaust gas recirculation system.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Bei der Verteilereinspritzpumpe wird ein Pump- und Verteilerkolben 1 durch eine Antriebswelle 2 und mit Hilfe eines Nockengetriebes 3 in eine hin- und hergehende und gleichzeitig rotierende Bewegung versetzt. Bei jedem Druckhub des Pumpenkolbens 1 wird dabei aus einem Pumpenarbeitsraum 4 über eine Verteilerlängsnut 5 Kraft­stoff zu einem von mehreren Druckkanälen 6 gefördert, die um den Pump- und Verteilerkolben 1 herum in gleich­mäßigen Drehwinkelabständen angeordnet sind und jeweils zu einem nicht dargestellten Brennraum einer Brennkraft­maschine führen. Der Pumpenarbeitsraum 4 wird über einen Saugkanal 7 aus einem im Gehäuse der Einspritzpumpe vorhandenen und mit Kraftstoff gefüllten Saugraum 8 mit Kraftstoff versorgt, indem während des Saughubs des Pump- und Verteilerkolbens 1 der Saugkanal 7 durch im Pumpenkolben 1 vorgesehene Steuerlängsnuten 9 aufge­steuert wird. Die Anzahl der Steuernuten 9 enspricht der Anzahl der Druckkanäle 6 und damit der Anzahl der bei einer Umdrehung des Pumpenkolbens ausgeführten Druckhübe. In dem Saugkanal 7 ist ein Magnetventil 10 angeordnet, das zur Beendigung der Einspritzung den Saugkanal 7 sperrt, so daß während des Saughubs des Pumpenkolbens 1 kein Kraftstoff aus dem Saugraum 8 in den Pumpenarbeitsraum 4 gelangen kann.In the case of the distributor injection pump, a pump and distributor piston 1 is set in a reciprocating and simultaneously rotating movement by a drive shaft 2 and with the aid of a cam gear 3. With each pressure stroke of the pump piston 1, fuel is conveyed from a pump work chamber 4 via a longitudinal distribution groove 5 to one of a plurality of pressure channels 6, which are arranged around the pump and distributor piston 1 at uniform angular intervals and each lead to a combustion chamber (not shown) of an internal combustion engine. The pump work chamber 4 is supplied with fuel via a suction channel 7 from a suction chamber 8 which is present in the housing of the injection pump and is filled with fuel, in that the suction channel 7 is opened during the suction stroke of the pump and distributor piston 1 by longitudinal control grooves 9 provided in the pump piston 1. The number of control grooves 9 corresponds to the number of pressure channels 6 and thus the number of pressure strokes carried out with one revolution of the pump piston. In the suction channel 7, a solenoid valve 10 is arranged, which closes the suction channel 7 at the end of the injection, so that no fuel can get from the suction chamber 8 into the pump working chamber 4 during the suction stroke of the pump piston 1.

Die pro Hub in den Druckkanal 6 geförderte einzuspritzen­de Menge wird durch die axiale Lage eines um den Pumpen­kolben 1 angeordneten Regelschiebers 11 bestimmt. Diese axiale Lage wird durch einen Drehzahlregler 12 und einen willkürlich betätigbaren Verstellhebel 13 bestimmt unter Auswertung der jeweiligen Drehzahl und Last (die Last kann beispielsweise der Stellung des Gaspedals des Kraftfahrzeugs entsprechen).The quantity to be injected into the pressure channel 6 per stroke is determined by the axial position of a control slide 11 arranged around the pump piston 1. This axial position is determined by a speed controller 12 and an arbitrarily actuated adjusting lever 13, evaluating the respective speed and load (the load can correspond, for example, to the position of the accelerator pedal of the motor vehicle).

Der Saugraum 8 wird von einer Förderpumpe 14 her mit Kraftstoff versorgt, die durch die Antriebswelle 2 angetrieben wird und aus einem Kraftstoffbehälter 15 und einer Saugleitung 16 Kraftstoff zuführt. Durch ein Drucksteuerventil 17 wird der Ausgangsdruck der Förderpumpe 14 und damit der Druck im Saugraum 8 gesteu­ert, wobei dieser Druck mit zunehmender Drehzahl ent­sprechend einer gewünschten Funktion ebenfalls zunimmt. Im Saugraum 8 sind der Nockentrieb 3 sowie der Drehzahl­regler 12 angeordnet, die somit allseitig von diesem Druck beaufschlagt sind und von diesem Kraftstoff ge­schmiert werden.The suction chamber 8 is supplied with fuel by a feed pump 14, which is driven by the drive shaft 2 and supplies fuel from a fuel tank 15 and a suction line 16. The output pressure of the feed pump 14 and thus the pressure in the suction chamber 8 is controlled by a pressure control valve 17, this pressure also increasing with increasing speed in accordance with a desired function. The cam mechanism 3 and the speed controller 12 are arranged in the suction chamber 8 and are thus acted upon on all sides by this pressure and are lubricated by this fuel.

Der durch die Antriebswelle 2 angetriebene Nockentrieb 3 weist einen Rollen 18 tragenden Rollenring 19 auf, der um einen bestimmten Winkel verdrehbar im Gehäuse gelagert ist und in dessen U-förmigen Querschnitt die Rollen 18 gelagert sind. Dieser Rollenring 19 ist über einen Verstellbolzen 21 mit einem Spritzverstellkolben 22 verdrehschlüssig gekoppelt, wobei in der Zeichnung dieser Spritzverstellkolben 22 um 90° verdreht darge­stellt ist, d.h. tatsächlich senkrecht zur Darstellungs­ ebene verstellbar ist. In der Innenbohrung dieses Rollen­rings 19 ist eine Klauenkupplung vorhanden, bei der abtriebsseitige Klauen 23 der Antriebswelle 2 mit an­triebsseitigen Klauen 24 des Pump- und Verteilerkolbens 1 ineinandergreifen, so daß der Pump- und Verteilerkolben 1 unabhängig von der Antriebswelle 2 eine Hubbewegung während des Rotierens ausüben kann. Am Pumpenkolben 1 ist eine Stirnnockenscheibe 25 angeordnet, die mit ihrer Stirnnocken 26 aufweisenden Stirnfläche auf den Rollen 18 abläuft, wobei die Zahl der Stirnnocken wiede­rum der Anzahl der Druckkanäle 6 entspricht. Die Stirn­nockenscheibe 25 wird durch Federn 27, von denen nur eine dargestellt ist, mit ihrer Laufbahn auf die Rollen 20 gepresst.The cam drive 3, which is driven by the drive shaft 2, has a roller ring 19 which carries rollers 18 and which is rotatably mounted in the housing by a certain angle and in the U-shaped cross section of which the rollers 18 are mounted. This roller ring 19 is coupled in a rotationally locking manner to an injection adjustment piston 22 via an adjustment bolt 21, this injection adjustment piston 22 being shown rotated by 90 ° in the drawing, ie actually perpendicular to the illustration level is adjustable. In the inner bore of this roller ring 19 there is a claw coupling in which the claws 23 on the output side of the drive shaft 2 mesh with the claws 24 on the drive side of the pumping and distributing piston 1, so that the pumping and distributing piston 1 independently of the drive shaft 2 exert a lifting movement while rotating can. An end cam disk 25 is arranged on the pump piston 1 and runs with its end cam 26 on the rollers 18, the number of end cams in turn corresponding to the number of pressure channels 6. The end cam disk 25 is pressed with its track onto the rollers 20 by springs 27, only one of which is shown.

Der tangential zum Rollenring axial verschiebbare Spritz­verstellkolben 22 ist in der einen Verstellrichtung durch eine Rückstellfeder 28 belastet und in der anderen Verstellrichtung durch den in einem Raum 29 herrschenden Druck des Saugraums 8, welcher durch einen im Spritzver­stellkolben 22 vorhandenen Drosselkanal 31 übertragen wird. Die Verschieberichtung des Spritzverstellkolbens ist dabei so gewählt, daß wenn der Kraftstoffdruck im Saugraum 8 mit zunehmender Drehzahl steigt, der Spritzverstellkolben 22 entgegen der Rückstellfeder 28 verschoben den Rollenring 19 so verdreht, daß die Stirnnocken 26 der Stirnnockenscheibe 25 früher mit den Rollen 18 in Eingriff gelangen, wodurch der Hubbeginn des Pumpenkolbens 1 und damit der Förderbeginn des Kraftstoffes in bezug auf die Drehlage der Antriebswelle 2 vorverlegt wird. Je höher also die Drehzahl ist, desto früher ist der Förderbeginn (Spritzbeginn).The injection adjustment piston 22, which is axially displaceable tangentially to the roller ring, is loaded in one adjustment direction by a return spring 28 and in the other adjustment direction by the pressure of the suction space 8 prevailing in a space 29, which is transmitted through a throttle channel 31 present in the injection adjustment piston 22. The direction of displacement of the injection adjustment piston is chosen so that when the fuel pressure in the suction chamber 8 increases with increasing speed, the injection adjustment piston 22 is displaced counter to the return spring 28 and rotates the roller ring 19 so that the end cams 26 of the end cam disk 25 come into engagement with the rollers 18 earlier , whereby the start of the stroke of the pump piston 1 and thus the start of delivery of the fuel with respect to the rotational position of the drive shaft 2 is brought forward. So the higher the speed, the earlier the start of delivery (start of spraying).

Der Antrieb des Drehzahlreglers 12 erfolgt über ein Zahnrad 32, das mit der Antriebswelle 2 verbunden ist und einen Drehzahlgeber 33 mit Fliehgewichten 34 an­treibt, welche an einer Reglermuffe 35 einerseits an­greifen, die axial verschiebbar auf einer Achse 36 gelagert ist und an der andererseits das durch eine Regelfeder 37 belastete Regelhebelsystem 38 angreift, welches den Regelschieber 11 für seine Hublage anlenkt. Das Regelhebelsystem 38 ist auf einer Achse 39 hierfür schwenkbar gelagert. Die Vorspannung der Regelfeder 37 ist durch den Verstellhebel 13 änderbar und zwar in der Art, daß bei Verstellung des Verstellhebels 13 in Richtung zunehmender Last auch die Vorspannung der Regelfeder 37 zunimmt, so daß der Regelschieber 11 weiter nach oben geschoben wird, was aufgrund eines dadurch gegebenen späteren Aufsteuerns eines Entlastungs­kanals 41 des Pumpenarbeitsraums 4 während des Druckhubs des Pumpenkolbens 1 eine Zunahme der Einspritzmenge zur Folge hat. Die Absteuerung der noch im Pumpenarbeits­raum 4 befindlichen Kraftstoffmenge ist immer dann gegeben, wenn während des Druckhubs des Pumpenkolbens 1 die Mündungen 42 des Entlastungskanals 1 aus dem Regelschieber 11 austauchen und so die weitere Kraft­stoffförderung des Pumpenkolbens 1 in den Saugraum 8 erfolgt.The speed controller 12 is driven via a gear wheel 32 which is connected to the drive shaft 2 and drives a speed sensor 33 with flyweights 34 which, on the one hand, engage a control sleeve 35 which is axially displaceably mounted on an axis 36 and on the other hand by a control spring 37 attacks the control lever system 38, which links the control slide 11 for its stroke position. The control lever system 38 is pivotally mounted on an axis 39 for this purpose. The bias of the control spring 37 can be changed by the adjusting lever 13 in such a way that when the adjusting lever 13 is moved in the direction of increasing load, the bias of the control spring 37 also increases, so that the control slide 11 is pushed further up, which is due to a given later opening of a relief channel 41 of the pump work space 4 during the pressure stroke of the pump piston 1, an increase in the injection quantity results. The control of the amount of fuel still in the pump working chamber 4 is always given when the orifices 42 of the relief channel 1 emerge from the control slide 11 during the pressure stroke of the pump piston 1 and the further fuel delivery of the pump piston 1 into the suction chamber 8 takes place.

Um den Förderbeginn, der wie bisher beschrieben nur drehzahlabhängig geändert wird, auch lastabhängig zu steuern, ist in der Verstellmuffe 35 eine Steuerbohrung 43 vorhanden, die mit einem in der Achse 39 verlaufenden Abflußkanal 44 zusammenwirkt, wodurch entweder in be­stimmten Lastzuständen, die sich über den Verstellhebel 13, die Regelfeder 37 und das Regelhebelsystem 38 auf die Regelmuffe 35 auswirken oder in bestimmten Fällen der Belastung des Motors, die sich auf die Drehzahl auswirkt, indem über die Fliehgewichte 34 eine Verstel­lung der Regelmuffe 35 erfolgt, durch das Aufsteuern des Abflußkanals 44 durch die Steuerbohrung 43 der Druck im Saugraum 8 verringert und damit der Förderbeginn auf später gestellt wird.In order to control the start of delivery, which, as previously described, is only changed as a function of speed, also as a function of load, there is a control bore in the adjusting sleeve 35 43 available, which cooperates with a drain channel 44 extending in the axis 39, which either in certain load conditions, which affect the control sleeve 35 via the adjusting lever 13, the control spring 37 and the control lever system 38, or in certain cases the load on the engine, the affects the speed by adjusting the control sleeve 35 via the centrifugal weights 34, by opening the discharge channel 44 through the control bore 43 the pressure in the suction chamber 8 is reduced and the delivery start is thus set to later.

Dieses Aufsteuern des Abflußkanals findet immer unterhalb einer bestimmten Last statt. Aus diesem Grunde wird der abfließende Kraftstoff zur Steuerung der Abgasrück­führung verwendet, die ebenfalls unterhalb einer be­stimmten Last eingeschaltet werden soll. Diese Spritz­beginnspätverstellung bei niederer Last dient unter anderem auch dazu, die NOx-Emission zu reduzieren, was allerdings zur Folge hat, daß die Kohlenwasserstoff-­Emission (HC) ansteigt. Die NOx-Emission wird zusätzlich durch die Abgasrückführung reduziert. Die Folge sind allerdings eine leichte Verschlechterung des Kraftstoff­verbrauchs der Brennkraftmaschine und der HC-Emission, sowie die Gefahr von Schwarzrauchbildung. Aus diesen Gründen wird die Abgasrückführung nur unterhalb einer bestimmten Last (Einspritzmenge pro Hub) durchgeführt.This opening of the drain channel always takes place below a certain load. For this reason, the outflowing fuel is used to control the exhaust gas recirculation, which should also be switched on below a certain load. This late start of spraying at low load also serves, among other things, to reduce the NO x emission, which, however, has the consequence that the hydrocarbon emission (HC) increases. NO x emissions are also reduced by exhaust gas recirculation. However, the result is a slight deterioration in the fuel consumption of the internal combustion engine and HC emissions, and the risk of black smoke formation. For these reasons, exhaust gas recirculation is only carried out below a certain load (injection quantity per stroke).

Der Abflußkanal 44 ist über eine Abflußleitung 45 mit dem Kraftstoffbehälter 15 verbunden, wobei in dieser Abflußleitung ein Druckhalteventil 46 angeordnet ist. Stromauf dieses Druckhalteventils 46 ist mit der Abfluß­leitung 45 ein hydraulischer Stellmotor 47 eines pneuma­tischen 3/2-Wegeventils 48 verbunden. Das Wegeventil 48 steuert eine Unterdruckleitung 49, die von einem Abgasrückführventil 51 zu einer Unterdruckquelle 52 führt. Das in Schließrichtung durch eine Feder 53 be­lastete Abgasrückführventil 51 ist in einer Abgasrück­führleitung 54 eines Motors 55 angeordnet, der über eine Einspritzleitung 56 vom Druckkanal 6 her mit Kraft­stoff versorgt wird, der in der oben beschriebenen Art gefördert wird bei entsprechender Regelung der Menge und des Förderbeginns. Die Abflußleitung 45 weist einen Bypass 57 auf, in dem eine Staudrossel 58 angeord­net ist.The drain channel 44 is connected via a drain line 45 to the fuel tank 15, in which Drain line a pressure control valve 46 is arranged. Upstream of this pressure-maintaining valve 46, a hydraulic servomotor 47 of a pneumatic 3/2-way valve 48 is connected to the discharge line 45. The directional control valve 48 controls a vacuum line 49, which leads from an exhaust gas recirculation valve 51 to a vacuum source 52. The exhaust gas recirculation valve 51, which is loaded in the closing direction by a spring 53, is arranged in an exhaust gas recirculation line 54 of an engine 55, which is supplied with fuel via an injection line 56 from the pressure channel 6, which is delivered in the manner described above, with appropriate regulation of the quantity and the start of delivery . The drain line 45 has a bypass 57 in which a throttling throttle 58 is arranged.

Die Abgasrückführsteuerung findet so statt, daß unterhalb einer bestimmten Last, bei der die Steuerbohrung 43 den Abflußkanal 44 aufsteuert, der dort aus dem Saugraum 8 und in die Abflußleitung 45 abfließende Kraftstoff dort durch die Staudrossel 58 gestaut wird bis ab Errei­chen eines bestimmten Druckes das Druckhalteventil 46 öffnet und unter Halten dieses Abflußdruckes den Kraftstoff in den Kraftstoffbehälter 15 abströmen läßt. Kurz vor Erreichen dieses Abflußdruckes wird durch den hydraulischen Stellmotor 47 das pneumatische Wege­ventil 48 geöffnet, so daß über die Unterdruckleitung 49 das Abgasrückführventil 51 durch die Unterdruckquelle 52 entgegen der Kraft der Schließfeder 53 geöffnet wird und Abgas über die Abgasrückführleitung 54 von der Abgasseite des Motors zur Saugseite strömen kann. Sobald dann bei Überschreiten des erforderlichen Lastzu­standes durch die Regelmuffe 35 wieder der Abflußkanal 44 geschlossen wird, baut sich über die Staudrossel 58 der Abflußdruck in der Abflußleitung 45 wieder ab, so daß der hydraulische Stellmotor 47 das Wegeventil 48 und damit das Abgasrückführventil 51 sperrt.The exhaust gas recirculation control takes place in such a way that below a certain load at which the control bore 43 opens the drain channel 44, the fuel flowing there out of the suction chamber 8 and into the drain line 45 is stowed there by the throttling throttle 58 until the pressure control valve reaches a certain pressure 46 opens and allows the fuel to flow into the fuel tank 15 while maintaining this discharge pressure. Shortly before this discharge pressure is reached, the pneumatic directional valve 48 is opened by the hydraulic servomotor 47, so that the exhaust gas recirculation valve 51 is opened by the vacuum source 52 against the force of the closing spring 53 via the vacuum line 49 and exhaust gas by the exhaust gas recirculation line 54 from the exhaust side of the engine can flow to the intake side. As soon as the discharge channel 44 is closed again when the required load state is exceeded by the control sleeve 35, the discharge pressure in the discharge line 45 builds up again via the throttle throttle 58, so that the hydraulic servomotor 47 blocks the directional control valve 48 and thus the exhaust gas recirculation valve 51.

Alle in der Beschreibung, den nachfolgenden Ansprüchen und der Zeichnung dargestellten Merkmale können sowohl einzeln, als auch in beliebiger Kombination miteinander erfindungswesentlich sein.All of the features shown in the description, the following claims and the drawing can be essential to the invention both individually and in any combination with one another.

Claims (6)

1. Abgasrückführeinrichtung für Brennkraftmaschinen mit einem in einer die Abgasleitung mit der Saug­leitung einer Brennkraftmaschine verbindenden Abgas­rückführleitung angeordneten, durch ein Steuermedium betätigten Abgasrückführventil, mit einem einen Stellmotor aufweisenden Wegeventil für das Steuermedium, mit einer Kraftstoffeinspritzanlage, bei der für einen eine Mindestlast und -drehzahl aufweisenden Kennfeldbereich ein hydraulischer Steuerdruck verfüg­bar ist
und mit einer den Stellmotor des Wegeventils steuern­den Einrichtung, in der der hydraulische Steuerdruck zu einer Stellgröße des Stellmotors verarbeitet wird,
dadurch gekennzeichnet, daß der Stellmotor des Wege­ventils (48) hydraulisch arbeitet, und daß der hydrau­lische Steuerdruck unmittelbar zur Betätigung des Wegeventils (48) dient.1.Exhaust gas recirculation device for internal combustion engines with an exhaust gas recirculation valve, which is arranged in an exhaust gas recirculation line and connects the exhaust pipe with the suction line of an internal combustion engine, with a directional valve for the control medium, which has a servomotor, with a fuel injection system, in which the control valve has a minimum load and speed Map area a hydraulic control pressure is available
and with a device controlling the servomotor of the directional control valve, in which the hydraulic control pressure is processed to a manipulated variable of the servomotor,
characterized in that the servomotor of the directional control valve (48) operates hydraulically and that the hydraulic control pressure is used directly to actuate the directional control valve (48). 2. Abgasrückführeinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß das Abgasrückführventil (51) als nicht betätigt geschloßenes, unterdruckgesteuertes Ventil ausgebildet ist, daß als Steuermedium Luft einer Unterdruckquelle (52) dient, und daß das Wege­ventil (48) als Pneumatikventil mit hydraulischem Stellmotor (47) ausgebildet ist.2. Exhaust gas recirculation device according to claim 1, characterized in that the exhaust gas recirculation valve (51) is designed as a non-actuated closed, vacuum-controlled valve, that air serves as a control medium, a vacuum source (52), and that the directional control valve (48) as a pneumatic valve with a hydraulic servomotor ( 47) is formed. 3. Abgasrückführeinrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der hydraulische Steuer­druck einer Einrichtung für eine drehzahl- und lastab­hängige Förderbeginnverstellung der Einspritzanlage entnehmbar ist.3. Exhaust gas recirculation device according to claim 1 or 2, characterized in that the hydraulic control pressure of a device for a speed and load-dependent delivery start adjustment of the injection system can be removed. 4. Abgasrückführeinrichtung mit einer Kraftstoffein­spritzpumpe insbesondere nach einem der vorhergehenden Ansprüche,
mit einem mit der Drehzahl zunehmenden, der Förder­beginnänderung dienenden, hydraulischen Druck mit einer lastabhängigen Änderung dieses hydrauli­schen Drucks in einem eine Mindestdrehzahl und -last­aufweisenden Kennfeld durch Abfließenlassen eines Teils einer Steuerflüssigkeit über ein last- und drehzahlabhängig gesteuertes Ventil, mit einer Staudrossel im Abflußstrom der Steuer­flüssigkeit und mit einer Steuereinrichtung zur Umsetzung des Staudruckes in eine Stellgröße für ein die Abgasseite mit der Saugseite einer Brennkraft­maschine verbindendes Abgasrückführventil, dadurch gekennzeichnet, daß parallel zur Staudrossel (58) ein Druckhalteventil (46) vorhanden ist, über das die Steuerflüssigkeit bei Einhaltung eines Stau­druckes abströmen.4. Exhaust gas recirculation device with a fuel injection pump in particular according to one of the preceding claims,
with a hydraulic pressure which increases with the speed and serves to change the start of delivery, with a load-dependent change in this hydraulic pressure in a map having a minimum speed and load by draining off part of a control liquid via a load- and speed-dependent valve, with a throttling valve in the flow of the control liquid and with a control device for converting the dynamic pressure into a manipulated variable for an exhaust gas recirculation valve connecting the exhaust side with the suction side of an internal combustion engine, characterized in that a pressure holding valve (46) is present parallel to the dynamic throttle (58), via which the control liquid flows out while maintaining a dynamic pressure . 5. Abgasrückführeinrichtung mit einer Kraftstoffein­spritzpumpe nach Anspruch 4, dadurch gekennzeichnet, daß als last- und drehzahlabhängig gesteuertes Ventil eine Regelmuffe (35) dient, die durch Fliehgewicht (34) entgegen der Kraft einer in der Vorspannung lastabhängig änderbaren Regelfeder (37) verschiebbar ist und über eine Steuerbohrung (43) die Steuer­flüssigkeit in einen Abflußkanal (44) austreten läßt.5. Exhaust gas recirculation device with a fuel injection pump according to claim 4, characterized in that a control sleeve (35) is used as a load- and speed-dependent valve, which can be displaced by centrifugal weight (34) against the force of a control spring (37) which can be changed as a function of the preload and lets the control fluid escape into a drainage channel (44) via a control bore (43). 6. Abgasrückführeinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Kraftstoff­einspritzanlage mit einer Verteilereinspritzpumpe arbeitet, deren Pump- und Verteilerkolben (1) relativ zur Antriebswelle (2) über eine Spritzverstellein­richtung zur Förderbeginnänderung drehverstellbar ist, und daß diese Relativverdrehung über einen hydraulisch betätigten Spritzverstellkolben (22) erfolgt, der in einen zwischen Antriebswelle (2) und Pump- und Verteilerkolben (1) angeordneten Nocken­trieb (3) eingreift und durch einen im Gehäuse der Verteilereinspritzpumpe in einem Saugraum (8) vorhan­denen drehzahlabhängig gesteuerten Kraftstoffdruck beaufschlagt wird.6. Exhaust gas recirculation device according to one of the preceding claims, characterized in that the fuel injection system works with a distributor injection pump, the pump and distributor piston (1) relative to the drive shaft (2) is rotatably adjustable via a spray adjustment device for the start of delivery change, and that this relative rotation via a hydraulically operated Injection-adjusting piston (22) takes place, which engages in a cam drive (3) arranged between the drive shaft (2) and the pump and distributor piston (1) and is acted upon by a speed-dependent controlled fuel pressure in the housing of the distributor injection pump in a suction chamber (8).
EP88118278A 1987-12-03 1988-11-03 Exhaust gas recirculation device for internal combustion engines Expired - Lifetime EP0318714B1 (en)

Applications Claiming Priority (2)

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DE3740968A DE3740968C1 (en) 1987-12-03 1987-12-03 Exhaust gas recirculation device for internal combustion engines
DE3740968 1987-12-03

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EP0318714A3 EP0318714A3 (en) 1990-02-14
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EP0318714B1 (en) 1994-02-23
KR970003154B1 (en) 1997-03-14
KR890010409A (en) 1989-08-08
EP0318714A3 (en) 1990-02-14
DE3887966D1 (en) 1994-03-31
JP2690335B2 (en) 1997-12-10
DE3740968C1 (en) 1988-12-15
US4907560A (en) 1990-03-13
JPH025750A (en) 1990-01-10

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