EP0732490B1 - Turboaufgeladene Dieselbrennkraftmaschine - Google Patents

Turboaufgeladene Dieselbrennkraftmaschine Download PDF

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Publication number
EP0732490B1
EP0732490B1 EP96301360A EP96301360A EP0732490B1 EP 0732490 B1 EP0732490 B1 EP 0732490B1 EP 96301360 A EP96301360 A EP 96301360A EP 96301360 A EP96301360 A EP 96301360A EP 0732490 B1 EP0732490 B1 EP 0732490B1
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EP
European Patent Office
Prior art keywords
venturi
flow
engine
diesel engine
flow line
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP96301360A
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English (en)
French (fr)
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EP0732490A2 (de
EP0732490A3 (de
Inventor
Rod Radovanovic
A.S. Ghuman
Gregory H. Henderson
Angela R. May
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Cummins Inc
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Cummins Engine Co Inc
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Filing date
Publication date
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Publication of EP0732490A2 publication Critical patent/EP0732490A2/de
Publication of EP0732490A3 publication Critical patent/EP0732490A3/de
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Publication of EP0732490B1 publication Critical patent/EP0732490B1/de
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    • 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
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • 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
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/17—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the intake system
    • F02M26/19—Means for improving the mixing of air and recirculated exhaust gases, e.g. venturis or multiple openings to the intake system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
    • F02D9/12—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having slidably-mounted valve members; having valve members movable longitudinally of conduit
    • 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
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
    • 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
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/09—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine
    • F02M26/10—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine having means to increase the pressure difference between the exhaust and intake system, e.g. venturis, variable geometry turbines, check valves using pressure pulsations or throttles in the air intake or exhaust system
    • 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
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/17—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the intake system
    • F02M26/21—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the intake system with EGR valves located at or near the connection to the intake system

Definitions

  • the present invention relates in general to the routing and flow path for recirculating exhaust gas (EGR) and the routing and flow path for blow-by (crankcase vent) gas. More specifically the present invention relates to the use of a control valve in cooperation with a venturi design in the flow path to introduce exhaust gases into the intake manifold in a mix with fresh charge air from the turbocharger.
  • EGR exhaust gas
  • blow-by blow-by
  • blow-by (crankcase vent) gas of medium and heavy duty diesel engines is typically vented to the atmosphere.
  • this gas is recirculated into the fresh charge air.
  • the expected legislation will likely be similar if not the same as what is now in effect for gasoline engines and light duty diesel engines.
  • blow-by gas In anticipation of such legislation, some thought must be given to where and how such blow-by gas can be integrated into the air/gas flow network.
  • routing the blow-by gas in front of the compressor of the turbocharger is not desirable due to fouling of the wheel and aftercooler by oily deposits and other particulate matter.
  • a venturi with a cooperating control valve, is placed in the flow path downstream of the aftercooler so as to induce the flow of blow-by gas into the fresh charge air.
  • the induced flow is created by having a low enough static pressure at the throat of the venturi.
  • venturi/control valve combination is placed in the flow path downstream of the aftercooler so as to induce the flow of EGR into the fresh charge air.
  • EGR Enhanced spasmodic satutica satutica satutica satutica satutica satutica satutica satutica satutica satutica satutica satutica satutica satutica satutica satutica satutica satutica satutica satutica satutica adamente, EPA and CARB.
  • NO x noxious oxides of nitrogen
  • One possibility for limiting or controlling the combustion temperature is to recirculate a portion of the exhaust gas (EGR) back to the engine air intake. Since the exhaust gas has a higher specific heat, the combustion mixture will burn at a lower temperature. The lower combustion temperature will, in turn, reduce the amounts of NO x produced during combustion.
  • EGR exhaust gas
  • Diesel engines differ from spark ignition engines in a number of important ways, one being that the diesel engine does not include a valved, or throttled, intake manifold into which the combustion air is induced through a throttle and valve. Accordingly, the vacuum pressure existing in a diesel engine intake duct is slight at most. The source of vacuum pressure provided by the intake manifold of a spark ignition engine is, therefore, not available in a diesel engine. Hence, any prior art control system utilizing the vacuum pressure as an input to the control system will not work with a diesel engine.
  • the engine speed under a given load is controlled by the quantity of fuel injected into the engine combustion chambers and accordingly the "throttle" of the diesel engine is considered to be a manually operated foot pedal connected by a linkage to a fuel pump for supplying the engine fuel injectors.
  • the foot operated pedal is actuated to govern the quantity of fuel delivered by the fuel pump to the combustion chambers of the engine and thus controls the engine speed under a given load. Since the quantity of fuel introduced into the combustion chamber varies, the production of NO x varies as a function of the throttle setting. This being the case, it is theoretically possible to control EGR in a diesel engine using only the throttle position as an input to the control system.
  • the present invention is therefore directed toward providing an EGR control system which utilizes only throttle position as an input to the control system. Such a control system could then be used with a diesel engine.
  • a venturi in another related embodiment of the present invention is placed in the fresh charge air flow line between the compressor and aftercooler and is connected to an exhaust gas flow line whose input side is connected between the exhaust manifold and the turbine. Static pressure at the throat of the venturi is sufficiently low so as to induce the flow of exhaust gas into the flow of fresh charge air.
  • US-A-5,333,456 discloses a turbocharged engine provided with a vacuum actuated control device for an exhaust gas recirculation control valve.
  • a venturi throat in the engine air intake passage generates a vacuum in response to air flow through the throat.
  • the control valve is a plug valve which is on one side of the venturi throat.
  • the plug valve is mounted at one end of a rod which slides in structure which forms the venturi throat.
  • the rod extends across the engine air intake passage and is attached to a vacuum responsive movable slide element at its other end.
  • the slide element is contoured to form the opposite throat surface.
  • FIG. 1 is a schematic illustration of a turbocharged diesel engine assembly including a venturi conduit in tire air flow path according to a typical embodiment of the present invention.
  • FIG. 2 is a schematic illustration of a turbocharged diesel engine assembly including a venturi conduit in the air flow path according to a typical embodiment of the present invention.
  • FIG. 3 is a diagrammatic illustration of an alternative configuration for placement of the FIG. 2 venturi conduit in the flow path.
  • FIG. 4 is a diagrammatic illustration of a flow tube and flow line arrangement which results in a venturi effect and which is suitable for use in either the FIG. 1 or FIG. 2 assemblies but does not form part of the present invention
  • FIG. 5 is a schematic illustration of a turbocharged diesel engine assembly with a venturi conduit in the air flow path according to a typical embodiment of the present invention.
  • FIG. 6 is a diagrammatic illustration of a control valve which is suitable for use in the flow path of the FIG. 5 assembly.
  • FIG. 7 is a diagrammatic illustration of a control valve design which is suitable for use in the FIG. 5 assembly.
  • FIG. 8 is a diagrammatic illustration of a variable flow rate venturi which may be used with any of the FIG. 1, FIG. 2 or FIG. 5 assemblies.
  • FIG. 9 is a diagrammatic illustration of a variable throat area venturi which is suitable for use with any of tire FIG. 1, FIG. 2 or FIG. 5 assemblies.
  • FIG. 10 is a perspective view of an EGR control valve as mounted to a venturi conduit in an embodiment of the present invention.
  • FIG. 1 there is illustrated a schematic representation of an air/exhaust flow network 10 for a highly turbocharged diesel engine 11.
  • the exhaust gas from the cylinders is directed to turbine 12 of the turbocharger 13.
  • the illustration of FIG. 1 is actually a turbocharged diesel engine assembly which includes the actual engine 11 as well as separate turbocharger 13, aftercooler 14, various flow lines and components.
  • Turbocharger 13 is of a conventional construction and operation. Its structure includes exhaust gas intake 13a, exhaust gas outlet 13b, air intake 13c, compressor 13d and compressed air outlet 13e.
  • Flow line 15 routes compressed air (fresh charge air) to the aftercooler 14 and from there via flow line 16 to tire intake manifold 17 of engine 11.
  • Flow line 18 connects the exhaust manifold to the turbine and flow line 18a is connected to flow line 18 as illustrated.
  • venturi conduit 19 Disposed in flow line 16 is venturi conduit 19 and attached directly to the throat of the venturi is a control valve 19a.
  • Control valve 19a is placed in flow line 18a and is designed to deliver recirculating engine gas (EGR) to venturi 19 by means of the low static pressure of venturi 19.
  • Venturi conduit 19 may be configured with a fixed or variable throat area and it creates a low enough static pressure so as to induce the flow of EGR gas from flow line 18a into the flow of fresh charge air from aftercooler 14.
  • FIG. 2 there is illustrated a schematic representation of an air/exhaust flow network 20 for a highly turbocharged diesel engine 21.
  • the exhaust gas from the cylinders are directed to turbine 22 of turbocharger 23.
  • the illustration of FIG. 2 is actually a turbocharged diesel engine assembly which includes the actual engine as well as a separate turbocharger and other flow lines and components.
  • Turbocharger 23 is of a conventional construction and operation. Its structure includes exhaust gas intake 24, exhaust gas outlet 25, air intake 26, compressor 27 and compressed air outlet 28. Flow line 32 routes the compressed air (fresh charge air) to the aftercooler 33 and from there via flow line 34 to the intake manifold 35 of engine 21.
  • crankcase vent 39 delivers blow-by gas via flow line 40 to control valve 41a which is attached directly to the throat of venturi conduit 41 which is disposed within flow line 34.
  • Venturi conduit 41 may be configured with a fixed or variable throat area and it creates a low enough static pressure so as to induce the flow of blow-by gas from flow line 40 into the flow of fresh charge air from aftercooler 33.
  • Control valves 19a and 41a have a similar construction (see FIG. 10) and as indicated each is attached directly to the throat area of the corresponding venturi conduit. By attaching the control valve directly to the venturi two important advantages are realized. First, the valve temperature is reduced by mounting it to a relatively cool surface (air intake). Secondly, this mounting location is the optimal place for controlling the exhaust gas (or blow-by gas) delivery. The responsiveness of the control valve 19a, 41a between opened and closed conditions is critical and the direct attachment eliminates or at least dramatically reduces any line losses or delays. If the control valve is upstream from the venturi then the line between the two results in additional gas delivery to the venturi even after the control valve is closed.
  • Venturi 44 which is suitable for use as either venturi 19 or venturi 41 is disposed in a branch line 45 which splits off of flow line 34 (or flow line 16 in FIG. 1). Branch line 45 which incorporates the venturi 44 then rejoins flow line 34 (16) downstream of the venturi 44.
  • flow line 40 which delivers the blow-by gas to the low pressure throat of the venturi 44 is shown as intersecting the sidewall of venturi 44.
  • flow line 34 which delivers the blow-by gas to the low pressure throat of the venturi 44 is shown as intersecting the sidewall of venturi 44.
  • only a smaller portion of the entire fresh charge air in flow line 34 is split into branch line 45 and flows through venturi 44.
  • Butterfly valve 46 disposed in flow line 34 is used to control the amount of gas flowing to venturi 44.
  • FIG. 4 represents a relatively simple way to introduce EGR gas into the flow of fresh charge air in flow line 16 (FIG. 1) or blow-by gas into the flow of fresh charge air in flow line 34 (FIG. 2).
  • a small pipe 50 inserted into flow line 34 and directed in a downstream direction, blow-by gas is drawn into the flow of fresh charge air.
  • pipe 50 acts as a type of ejector, flow is still the result of pressure differences.
  • the pressure drop which is part of the flow of the fresh charge air creates enough of a pressure drop relative to the pressure in pipe 50 for a suction action. to occur and for the blow-by gas to be drawn from the small pipe 50 into flow line 34.
  • the FIG. 4 arrangement would be used without any control valve such as valve 41a; however, the use of a control valve (see FIG. 10) is believed to represent the preferred arrangement.
  • FIG. 5 there is illustrated a schematic representation of an alternative EGR system 55 for a highly turbocharged diesel engine 56 which embodies the present invention.
  • EGR system 55 is configured in several respects in a manner similar to flow networks 10 and 20. The most notable differences are the positioning of the venturi conduit 57 upstream of the aftercooler 58 and the addition of flow line 59 and filter 60.
  • Control valve 61 is attached directly to the throat of the venturi conduit 57.
  • the cylinder exhaust from engine 56 (exhaust manifold) flows into the turbine 66 of turbocharger 67.
  • Flow line 59 is a branch line off of flow line 69 and intersects flow line 69 upstream of the turbocharger 67.
  • Flow line 59 routes exhaust gas first through filter 60 and then through control valve 61 and finally to venturi 57.
  • flow line 59 is in fact arranged in two sections, the same reference number has been used to indicate a single flow path from flow line 69 to venturi 57.
  • Flow line 70 from compressor 71 carries compressed air (fresh charge air) to venturi 57.
  • the output side of venturi 57 flows into aftercooler 58 and from there to intake manifold 72.
  • Venturi 57 By using a venturi 57 (with either a fixed or variable throat area) downstream of the compressor 71, static pressure at the throat can be sufficiently low to induce the flow of exhaust gas. Venturi 57 may be made of aluminum or other low cost material because it is not subject to high mechanical loading unlike the compressor wheel.
  • a small filter 60 which can be either self-regenerating at high loads or electrically regenerated, fouling of the aftercooler 58 can be eliminated. In the case of fairly clean exhaust gas, the filter 60 can be omitted. This system also allows for only one heat exchanger of the intake air instead of having another small heat exchanger in the EGR loop.
  • Cooled EGR helps maintain a higher air/fuel ratio so that with the introduction of exhaust gas into the fresh charge air there is no increase or only a very small increase in particulate, thus resulting in better NO x --particulate trade-off than without cooled EGR.
  • control valve 61 In order to control when EGR is introduced into the fresh charge air there is a control valve 61.
  • This valve can be solenoid operated and controlled by the central electronic control unit (ECU), thus providing EGR as a function of speed and load. If the engine does not have an electronic fuel injection system, it would be quite expensive to have an ECU and appropriate sensors just for control of EGR. In this case by providing a simple spring biased control valve (see FIGS. 6 and 7) the exhaust gas flows into the fresh charge air, via venturi 57, at and above a predetermined pressure in the exhaust manifold.
  • ECU central electronic control unit
  • a closing flap or plate 76 is placed at an angle and hinged within the flow line 77.
  • the flow line 77 which receives control valve 75 is effectively the same as flow line 59.
  • Plate 76 is spring biased by means of spring 78 and piston 79. Whenever the line pressure of the exhaust gas from the exhaust manifold is sufficient to overcome the predetermined spring force, exhaust gas is allowed to flow into the fresh charge air from the turbocharger 67 via the venturi 57. In effect a predetermined pressure in the exhaust manifold is selected as the threshold for the introduction of exhaust gas into the venturi and the spring bias is set accordingly.
  • venturi style of venturi 57 as used in system 55 may have a fixed or variable throat area and otherwise be of conventional construction as would be known to a person of ordinary skill in the art. It is also an option to replace venturi 57 with either of the venturi styles or arrangements of FIGS. 3 and 4. While the small pipe arrangement of FIG. 4 is not shaped as a narrow throated venturi conduit or nozzle, there is a pressure difference which influences the flow of exhaust (or blow-by) gas into the primary flow of fresh charge air.
  • Control valve 85 is positioned above flow line 86 (same as flow lines 59 and 77) which extends from the exhaust manifold of engine 56 to venturi 57.
  • An enclosed spring chamber 87 receives a bias spring 88 which acts on a diaphragm piston 89 having as a piston arm a connected flow-blocking plate 90 that extends into and across flow line 86.
  • Plate 90 is sized and shaped to block the flow of exhaust gas unless a sufficient boost pressure is seen by diaphragm 91.
  • conduit 92 the intake manifold boost pressure acts on diaphragm 91.
  • the spring biasing force is predetermined at a level which correlates to a predetermined boost pressure.
  • boost pressure When that pressure is exceeded the spring force is overcome and the diaphragm pushed upwardly, lifting plate 90 which in turn enables some flow through flow line 86.
  • exhaust gas recirculation is proposed as a means of reducing NO x in medium and heavy duty turbocharged diesel engines.
  • the exhaust gas will flow from the exhaust side to intake side through a simple tube if the exhaust side pressure is greater than the intake side pressure.
  • the intake side pressure is either about the same as the exhaust-side pressure or greater than the exhaust-side pressure.
  • the intake side static pressure can be reduced by accelerating the intake-side flow through a venturi. Connecting the EGR tube to the venturi throat will increase the pressure differential from the exhaust to intake side which will enhance the EGR flow rates and increase the number of engine operating conditions where EGR is possible.
  • This is basically the technical foundation or theory as embodied by systems 10 and 55 and the designs of venturis 19 and 57 (and the venturi design variations of FIGS. 3 and 4) and control valves 75 and 85.
  • a suitable control system for directing the operation of the control valve.
  • EGR control algorithm EGR control algorithm
  • the output of a throttle position sensor (TPS) is used as an input to two parallel filters where the TPS outputs a voltage proportional to rack position.
  • the first filter is a lag-lead compensated filter which functions as a differentiator, producing an output proportional to the instantaneous rate of change of the throttle position.
  • the second filter is a fixed-rate tracking filter which generates a tracking signal that tracks the input signal. The tracking signal, however, cannot vary by more than a maximum predetermined rate.
  • the output of the second filter is the difference between the input signal and the tracking signal.
  • the outputs of the two filters are summed and applied to a hysteretic comparator, which turns the EGR control valve off (closed) when the sum exceeds an upper threshold and turns the EGR control valve back on (open) when the sum has decayed below a lower threshold. If the TPS rate of change is above a certain threshold value, transient response and acceleration smoke will be unacceptable with EGR on due to air-limited operation. Therefore, above that value the EGR valve will be closed.
  • the algorithm also determines when to open the EGR valve after it has been closed by a sudden up-fueling to obtain maximums NO x benefit without a particulate/smoke penalty. the EGR valve is also closed at full throttle (determined by the TPS position) for maximum engine power output. Accordingly, the first filter output is largely responsible for triggering the EGR valve to turn off, while the second filter output is responsible for determining how long the EGR valve remains off.
  • An alternative control system design which is suitable for the present invention would include a first signal processor which is operable to produce a first output signal based upon a rate of change of an input signal and a second signal processor operable to produce a second output signal which tracks the input signal over time.
  • the second signal processor output signal does not exceed a predetermined maximum rate of change and the system output signal comprises a summation of tire first signal processor output signal and the second signal output signal.
  • a suitable control system includes an input port adapted to receive an input signal indicative of an engine operating parameter. There is a first signal processor operatively coupled to the input port which is operable to produce a first signal processor output signal based upon a rate of change of the input signal. A second signal processor which is operable to produce a second signal processor output signal tracks the input signal over time. The second signal processor output signal does not exceed a predetermined maximum rate of change. An output port is operatively coupled to the first and second signal processors and to the EGR control valve. The system output signal comprises a summation of the first signal processor output signal and the second signal processor output signal.
  • FIGS. 8 and 9 two further venturi designs which do not embody the present invention are illustrated. Each of these designs provide control over the EGR flow rate by controlling the pressure at the venturi throat.
  • venturi 95 is a variable mass flow or flow rate venturi. Venturi 95 is to be positioned similar to venturi 57 (see FIG. 5) downstream from the compressor and upstream from the aftercooler. Inlet 96 receives the fresh charge air from the compressor and this incoming flow is directed by a controllable diverter valve 97. Flow chamber 98 is separated by partition 99 into a by-pass path 100 and a venturi path 101. When the closing flap 102 of diverter valve 97 is moved all the way to the right (broken line position) the venturi path 101 is completely closed off from the incoming fresh charge air which flows through the by-pass path 100 to the aftercooler without the introduction of any EGR.
  • venturi path 101 When closing flap 102 is positioned all the way to the left so as to close off the by-pass path 100, the venturi path 101 is opened. As fresh charge air flows through the venturi path, the narrow throat 105 creates a venturi effect on the EGR which is present within flow line 106 coming from the exhaust manifold.
  • controllable diverter valve 97 is capable of being positioned at virtually any point in between the two extremes of all of the way to the left or all the way to the right.
  • closing flap 102 of the diverter valve When the closing flap 102 of the diverter valve is positioned between the end point extremes it will adjust or proportion the flow between the two flow paths 100 and 101.
  • the static pressure at the venturi throat and thus the differential pressure is set by controlling the mass flow through the venturi flow path.
  • the throat section of the venturi is sized to provide controllable EGR over the entire engine map.
  • Venturi arrangement 110 is positioned in a flow line 111 with an intake side 112 and an exit flow side 113.
  • the EGR flow line 114 intersects the flow line 111 as illustrated. The point of intersection is at a narrowed portion 115 of flow line 111; the narrowing being achieved by the placement of a narrowing sleeve in the flow line 111.
  • the remainder of venturi arrangement 110 includes guide rings 118, struts 119, actuator 120 and centerbody 121.
  • Centerbody 121 which is aerodynamically smooth is positioned within the slight area reduction section (portion 115) and is moveable axially relative to the area reduction section.
  • the static pressure at the venturi throat is controlled by changing the venturi area via the centerbody position.
  • the centerbody 121 is held by struts 119 to guide rings 118 which keep the centerbody in the center of the tube.
  • the rear guide ring is used as a shut-off valve.
  • the controlling actuator is located in the clean, up stream air.
  • venturi arrangements of FIG. 8 and 9 are suitable for use as the venturi of the FIG. 1 flow network 10 or the FIG. 2 flow network 20 or tire FIG. 5 flow system 55.
  • Venturi conduit 132 has an air flow inlet end 133 and an elongated body 134. Contoured on the interior of the elongated body is a venturi 135. The outlet end 136 is designed so as to be attachable directly to the intake manifold.
  • the control valve 130 mounts to a raised portion 140 of the elongated body 134 and a flow passageway 141 is defined by this raised portion 140 and is in direct flow communication with the control valve.
  • the control valve has an inlet port 142 which receives a flow of EGR or blow-by gas. Whether this flow of gas actually enters the venturi is controlled by the opened or closed state of the control valve based on a selected valve control system.
  • the gas which is allowed to flow passes through passageway 141 and from there into the throat 143 of the venturi.
  • the gas is actually introduced at an acute angle ( ⁇ ) into the venturi throat 143 and this provides a desireable balance between mixing of the gas flow and fresh charge air and the gas flow rate with a minimal effect on the pressure drop across the venturi.

Claims (5)

  1. Dieselmotoranordnung mit Turboladung, die einen Dieselmotor (11; 21; 56), einen Turbolader (13; 23; 67), eine Motorgasstromleitung (18, 18a; 40; 59; 77; 86; 114) von dem Dieselmotor (11; 21; 56), um Motorgas aus dem Dieselmotor zu leiten, und eine Stromleitung (15, 16; 32, 34; 70; 111) für frische Ladeluft von dem Turbolader (13; 23; 67) zu dem Dieselmotor (11; 21; 56), um frische Ladeluft von dem Turbolader zu dem Dieselmotor zu liefern;
    einen Venturi-Kanal (19; 41; 44; 57; 95; 110; 132), der in der Stromleitung (15, 16; 32, 34; 70; 111) für frische Ladeluft zwischen dem Turbolader (13; 23; 67) und dem Motor (11; 21; 56) angeordnet ist, wobei der Venturi-Kanal (19; 41; 44; 57; 95; 110; 132) ein Venturi-Halsgebiet (131) umfaßt und durch dieses einen Stromweg für frische Ladeluft bestimmt; und
    ein Regelventil (19a; 41a; 61; 75; 85; 130) aufweist, das an dem Venturi-Halsgebiet (131) befestigt ist, einen Durchlaß (141) durch dieses umfaßt und in Stromverbindung mit dem Stromweg durch den Venturi-Kanal (19; 41; 44; 57; 95; 110; 132) angeordnet ist, wobei der Durchlaß (141) in Stromverbindung mit der Motorgasstromleitung (18a; 40; 59) verbunden ist, wodurch Motorgas, das aus dem Dieselmotor (11; 21; 56) austritt und durch die Motorgasstromleitung (18, 18a; 40; 59; 77; 86; 114) strömt, fähig ist, aufgrund des niedrigen statischen Drucks, der durch das Venturi-Halsgebiet (131) erzeugt ist, mit frischer Ladeluft gemischt zu werden, wobei die Einleitung von Motorgas in den Venturi-Kanal (19; 41; 44; 57; 95; 110; 132) durch das Regelventil (19a; 41a; 61; 75; 85; 130) geregelt wird, dadurch gekennzeichnet, daß sich der Durchlaß (141) mit dem Stromweg an einer Stelle kreuzt, die mit dem Venturi-Halsgebiet (131) zusammenfällt und der Durchlaß (141) in einem spitzen Winkel (β) relativ zu dem Venturi-Kanal (19; 41; 57; 132) derart eingestellt ist, daß das Motorgas beim Betrieb mit einem Motorgasstrom durch den Durchlaß (141) und einem Strom frischer Ladeluft durch die Venturi-Rohrleitung (19; 41; 57; 132) in den Strom frischer Ladeluft in einem spitzen Winkel (β) eintritt.
  2. Dieselmotoranordnung mit Turboladung nach Anspruch 1, bei der die Diaselmotoranordnung mit Turboladung einen Nachkühler (14; 33; 58) in der Stromleitung (15; 32; 70; 111) für frische Ladeluft aufweist.
  3. Dieselmotoranordnung mit Turboladung nach Anspruch 2, bei der das Venturi-Halsgebiet (131) stromabwärts von dem Nachkühler (14, 33) zwischen dem Nachkühler (14; 33) und dem Motor (11; 21) angeordnet ist.
  4. Dieselmotoranordnung mit Turboladung nach Anspruch 2, bei der das Venturi-Halsgebiet (131) stromaufwärts von dem Nachkühler (58) zwischen dem Nachkühler (58) und dem Turbolader (67) angeordnet ist.
  5. Dieselmotoranordnung mit Turboladung nach Anspruch 4, bei der die Dieselmotoranordnung mit Turboladung einen Filter (60) in der Motorgasstromleitung (59) stromaufwärts von dem Venturi-Halsgebiet (131) aufweist.
EP96301360A 1995-03-14 1996-02-28 Turboaufgeladene Dieselbrennkraftmaschine Expired - Lifetime EP0732490B1 (de)

Applications Claiming Priority (2)

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US40405995A 1995-03-14 1995-03-14
US404059 1999-09-23

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EP0732490A2 EP0732490A2 (de) 1996-09-18
EP0732490A3 EP0732490A3 (de) 1997-08-13
EP0732490B1 true EP0732490B1 (de) 2001-04-11

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JP (1) JPH08270509A (de)
DE (1) DE69612420T2 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009020618A1 (de) 2009-05-09 2010-11-11 Daimler Ag Mischvorrichtung zum Zumischen eines Abgasrückführstroms in einen Ladeluftstrom einer Brennkraftmaschine
US11821389B2 (en) 2021-08-20 2023-11-21 Caterpillar Inc. Method and system for supplying fuel gas

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5974802A (en) * 1997-01-27 1999-11-02 Alliedsignal Inc. Exhaust gas recirculation system employing a fluidic pump
IT1291509B1 (it) * 1997-02-11 1999-01-11 Fiat Ricerche Motore a combustione a ciclo diesel, con ricircolo dei gas di scarico, provvisto di dispositivo miscelatore dei gas di ricircolo.
AT2539U1 (de) * 1997-12-22 1998-12-28 Avl List Gmbh Brennkraftmaschine mit mindestens einem abgasturbolader
FR2788565B1 (fr) * 1999-01-15 2001-02-09 Renault Vehicules Ind Collecteur d'admission comportant des moyens de raccordement a un circuit de recyclage des gaz d'echappement
US6408831B1 (en) * 2000-12-20 2002-06-25 Caterpillar Inc. System for controlling the temperature of an intake air
DE10226694A1 (de) * 2002-06-15 2003-12-24 Daimler Chrysler Ag Aufgeladene Brennkraftmaschine mit einer Kurbelgehäuseentlüftungseinrichtung
DE102006054956B4 (de) * 2006-11-22 2015-12-03 Man Diesel & Turbo Se Brennkraftmaschine
JP4986168B2 (ja) * 2008-07-10 2012-07-25 トヨタ自動車株式会社 ブローバイガス処理装置
JP5321088B2 (ja) * 2009-01-23 2013-10-23 トヨタ自動車株式会社 潤滑油回収装置
US8453626B2 (en) * 2011-08-26 2013-06-04 Concentric Skånes Fagerhult AB EGR venturi diesel injection
CN102953869A (zh) * 2012-11-27 2013-03-06 第一拖拉机股份有限公司 低排放直通外部冷却的废气再循环系统
JP6374804B2 (ja) * 2014-03-31 2018-08-15 株式会社クボタ エンジン
US10316803B2 (en) 2017-09-25 2019-06-11 Woodward, Inc. Passive pumping for recirculating exhaust gas
US10995705B2 (en) 2019-02-07 2021-05-04 Woodward, Inc. Modular exhaust gas recirculation system
CN213175878U (zh) 2020-01-08 2021-05-11 伍德沃德有限公司 排气气体再循环混合器和发动机系统
US11215132B1 (en) 2020-12-15 2022-01-04 Woodward, Inc. Controlling an internal combustion engine system
US11174809B1 (en) 2020-12-15 2021-11-16 Woodward, Inc. Controlling an internal combustion engine system

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3149454A (en) * 1961-08-16 1964-09-22 Motoren Werke Mannheim Ag Gas engines
FR2271394B1 (de) * 1974-05-15 1978-03-24 France Etat
DE3029435A1 (de) * 1978-07-19 1982-03-04 Walter 2105 Seevetal Franke Verfahren zum betrieb eines verbrennungskraftmotors, dieselmotors und verbrennungskraftmotor zur durchfuehrung des verfahrens
US4426848A (en) * 1981-11-20 1984-01-24 Dresser Industries, Inc. Turbocharged engine exhaust gas recirculation system
NL8401537A (nl) * 1984-05-11 1985-12-02 Tno Systeem en inrichting voor uitlaatgasrecirculatie bij verbrandingsmachine.
DE3831080C2 (de) * 1987-09-23 1996-06-20 Volkswagen Ag Abgasrückführung für eine Brennkraftmaschine
DE69130976T2 (de) * 1990-11-06 1999-07-08 Mazda Motor Abgasrückführungssystem für eine Brennkraftmaschine
DE4038918A1 (de) * 1990-12-06 1992-06-11 Porsche Ag Mischvorrichtung fuer gasfoermige medien von brennkraftmaschinen
US5333456A (en) * 1992-10-01 1994-08-02 Carter Automotive Company, Inc. Engine exhaust gas recirculation control mechanism
EP0653559A1 (de) * 1993-11-12 1995-05-17 Cummins Engine Company, Inc. Turbo-aufgeladene Dieselbrennkraftmaschinen

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009020618A1 (de) 2009-05-09 2010-11-11 Daimler Ag Mischvorrichtung zum Zumischen eines Abgasrückführstroms in einen Ladeluftstrom einer Brennkraftmaschine
US11821389B2 (en) 2021-08-20 2023-11-21 Caterpillar Inc. Method and system for supplying fuel gas

Also Published As

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JPH08270509A (ja) 1996-10-15
DE69612420D1 (de) 2001-05-17
DE69612420T2 (de) 2001-07-26
EP0732490A2 (de) 1996-09-18
EP0732490A3 (de) 1997-08-13

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