EP1149253B1 - Gasführungseinrichtung - Google Patents
Gasführungseinrichtung Download PDFInfo
- Publication number
- EP1149253B1 EP1149253B1 EP00902645A EP00902645A EP1149253B1 EP 1149253 B1 EP1149253 B1 EP 1149253B1 EP 00902645 A EP00902645 A EP 00902645A EP 00902645 A EP00902645 A EP 00902645A EP 1149253 B1 EP1149253 B1 EP 1149253B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- air
- pressure
- gas
- compensation
- 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
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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
- 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
- F02M26/65—Constructional details of EGR valves
- F02M26/66—Lift valves, e.g. poppet valves
- F02M26/68—Closing members; Valve seats; Flow passages
-
- 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
-
- 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
- F02M26/53—Systems for actuating EGR valves using electric actuators, e.g. solenoids
-
- 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
- F02M26/65—Constructional details of EGR valves
- F02M26/66—Lift valves, e.g. poppet valves
- F02M26/67—Pintles; Spindles; Springs; Bearings; Sealings; Connections to actuators
Definitions
- the invention relates to an air guide device with pressure compensation, such as it is described in claim 1, and a use of such Air guiding device as an air duct for an internal combustion engine an air loading device.
- Otto and diesel engines especially those of motor vehicles usually with gas routing devices, in particular exhaust gas recirculation valves (EGR valves). Through them the fresh gas sucked in partially mixed exhaust gas in order to reduce the NOx emission and to Improve fuel consumption and reduce noise.
- gas routing devices in particular exhaust gas recirculation valves (EGR valves).
- EGR valves exhaust gas recirculation valves
- air routing devices especially in connection with air charging devices of internal combustion engines.
- Such gas routing devices include metering devices or control devices, with which the amount of gas fed or returned depends on the operating point can be adjusted. Too little gas recirculation would be the desired Effects are missing, too great in the exhaust gas recirculation of gasoline engines malfunctions or an undesirable increase in HC or even CO emissions lead to an undesirable increase in diesel engines of particle emissions and excessive air recirculation would be the desired Make the state of charge unreachable.
- Such control devices are usually fully closable valves by a vacuum membrane or a servomotor or one against a spring working proportional magnets are set, which in turn have a Clock valve or a relay can be operated by the engine control unit.
- the one Information used in the control unit is usually that about load and Engine speed and the amount of air drawn in. To improve the Working will also be the feedback of the opening path via a path measuring system applied.
- the pressure gradient acts on the gas routing devices, as a rule between the pipe systems of the motor connected by them. It puts for the actuation of the metering device of the gas guide device Problem as it usually tries to move the metering device in the direction move, in which also the led or recirculated gas flows.
- WO 98/54460 describes an exhaust gas recirculation device for recycling Exhaust gas in a gas supply of engines with an exhaust gas supply, one Fresh gas supply and an outlet channel opening into the gas supply. Exhaust gas and fresh gas supply are connected via a control unit whose fresh gas side a pressure plate is provided, which the influence of occurring on the exhaust and Frsichgass side and on the exhaust gas flow impacting pressure fluctuations minimized.
- DE-C-196 39 146 discloses a diverter valve which is between a Intake air line and a compressor outlet line in an internal combustion engine is arranged with charge air device. To control the intake air conditions in overrun mode a control line is provided, which from Intake manifold behind the throttle valve a spring accumulator of the diverter valve ventilated.
- the invention in particular allows an actuator of the To be able to dimension the control member correspondingly smaller, with the consequence of Space and weight savings, lower power consumption and less Self-heating.
- the pressure drop of the air pressure over the control element can not a force component due to this compensation device lead in the direction of an unwanted opening or closing of the Control body acts, thereby the desired control of the enforced Gas quantity is significantly improved.
- one side of the Compensation device with the gas pressure on the compressed gas side and the other Side with the fresh gas side gas pressure is provided.
- the resulting Pressure difference across the compensation device results in a force component, which is opposite to the force component to be compensated has the same amount and thus the balance of the two power components causes.
- the compensation device can advantageously as a throttle valve, a double, ball, cone or cylinder valve is provided in the control member his.
- control element comprises a valve rod and a valve plate attached to it with a gas pressure effective Surface so that a valve disc force acts on the valve disc equal to the product of the gas pressure effective area and the pressure difference is.
- the compensation device comprises at least one piston, a member and / or a bellows, which is fixed to the valve rod and on whose gas pressure effective surface acts the pressure difference, so that a compensating force engages the valve rod, which compensates for the valve disc force.
- control member is through a mechanical, pneumatic, hydraulic, magnetic or electrical Actuating device or motor, in particular an electrical lifting magnet, actuated.
- a magnet or Proportional magnets proved that with such an opening or position of the control unit can be set very quickly and precisely. Because the positioning force in the case of a proportional magnet only approximately from the one flowing through Current, but not determined by the opening path, is also advantageously a quick response to control signals possible.
- the compensation device comprises an inner valve which is provided in the control member.
- a gas pressure in an internal valve compensation space is advantageously above the inner valve in connection with an opening gap between a piston the compensation device and a guide sleeve of the piston controllable and the inner valve from an actuating device and / or an inner valve actuating device actuated.
- the choice of the diameter of the piston relative to that of the Control element, for example of the main valve, also influences the tuning of the inner valve to the opening gap between the piston and the guide sleeve.
- the compensation device acts via a kinematic translation, in particular a lever translation, on the controller to make a difference between for gas pressure effective areas on the one hand of the control member and on the other hand of the compensation device to compensate.
- This translation translates from the Compensation device generated force component to a size for the Compensation of the force to be compensated is suitable for the control element. This is particularly advantageous if the areas effective for the gas pressures or the area of the compensation device and control unit differ.
- control member is a Spring action of a diaphragm or bellows biased in the closing direction, in particular, in addition, a spring to support the bias can be provided to an additional force component in the closing direction of the tax body.
- the compensation device and the control element connected to each other in an effective manner and controllable via the control device.
- the compensation device and forces generated by the actuator together act the tax body and add or compensate appropriately to exert the desired net force or force component on the tax body.
- control member has a device which always provides information about the respective opening cross-section of the Control body, e.g. a potentiometer. So that through the actuator set opening of the control member with a target opening be compared.
- the air guiding device advantageously also allows an air flow from the fresh air duct into the fresh air pressure duct by the control member, if in the fresh air pressure channel a lower gas pressure than in that Fresh air duct prevails.
- FIG 1 shows schematically parts of a fresh gas and exhaust system of an internal combustion engine with an exhaust gas recirculation gas guide device (exhaust gas recirculation device) a and a preferred fresh gas leading invention Air guiding device (which from now on is simply called a gas guiding device is designated) b.
- the inventive air guiding device is dashed in Figure 1 and indicated by b.
- the exhaust gas recirculation device is arranged between a fresh air guiding fresh air duct 2a and an exhaust gas guiding exhaust duct 5a and has an opening 1a which opens into an outlet duct 4a.
- the output channel 4a supplies a gas flow, which contains fresh gas and exhaust gas metered by the exhaust gas recirculation device, to an engine unit 100.
- the remaining, non-recirculated exhaust gas can escape from the internal combustion engine through an exhaust gas turbine 104.
- the exhaust gas turbine 104 is connected via a turbocharger shaft 106 to a compressor 102, which pumps fresh air from a fresh air duct 2b via a compressor inlet duct 4b into a compressor outlet duct 108.
- the fresh air duct 2b and the compressor inlet duct 4b are connected to an opening 1b of the air guiding device b.
- a control element of the air guiding device b separates the opening 1b from a fresh air pressure duct 5b.
- Figure 2 shows schematically a cross section of a first embodiment of the air or gas guide device according to the invention.
- fresh air is supplied via the fresh air duct 2b, which is described below is also referred to as fresh gas duct 2.
- the fresh air pressure duct 5 is via a valve or main valve 60, which consists of a valve plate 60A and a valve seat or wall 60B is connected to an orifice 1.
- the junction 1 is with the fresh gas duct 2 and the compressor inlet duct 4, which carries on the fresh gases mixed with the recirculated gas, connected.
- a compensation space or piston chamber 10 for receiving a compensation piston or compensating piston or piston 80 provided.
- the piston 80 is against his Circumference on a wall or side wall 11 and is via a spring or Coil spring 6 connected to an upper part of the wall 11.
- the piston chamber 10 is via a line or equalization line 12 with the junction 1 connected that the gas pressures in the piston chamber 10 and the mouth 1 can compensate quickly.
- Piston 80 and valve plate 60A are connected to one another via a rod 13.
- An actuating device is located on a side of the rod 13 opposite the piston 80 in the form of an electrical magnet or proportional magnet 14 arranged, via which the main valve 60 can be controlled or regulated.
- the gas pressure in the mouth 1 is p 3 or p 2 under operating conditions.
- the gas pressure p 5 or p 3 is present in the fresh air pressure channel 5 .
- the main valve 60 When used as an air guiding device, the main valve 60 is only opened in order to bring about a pressure equalization between p 2 and p 3 . In special cases this may also be desirable for p 2 > p 3 .
- the force acting in the rod 13 is strongly dependent on the pressure drop p 5 -p 3 or p 3 -p 2 via the main valve 60. Without piston 80 and without line 12, the force that would result from the pressure drop and a cross-sectional area or cross-section F 3 of valve plate 60A would act in rod 13: (p 3 - p 2 ) x F 3
- This force is compensated for by the piston 80, which has the same effective area or contact area F 3 for the gas pressure as the valve disk 60A. A force of the same amount counter to the force on the valve disk 60A thus acts on the piston 80.
- the actuation of the main valve 60 of the gas routing device is preferred essentially by the electric magnet or proportional magnet 14 achieved via the rod 13, the force in the proportional magnet 14 only depends on the coil current and not on the position of the armature.
- a Such an arrangement has the advantage that it responds quickly and has a valve lift or opening of the valve 60 can be adjusted very precisely. But it is also possible other operations of the main valve 60, such as mechanical, pneumatic, hydraulic and electromotive with the described Combine pressure compensation.
- FIG. 1 Another embodiment based on such pressure compensation the invention is shown in FIG.
- a metering or control member 61 find a throttle valve 61A which is connected to the rod 13 via a lever 15. It is advantageous here that the desired pressure compensation with the simplest mechanical design is possible. The disadvantage, however, is that the 61 A formed with the throttle valve Valve or main valve 61 is not hermetically gas-tight when closed is.
- FIG. 4 shows a further embodiment of the invention.
- a valve plate 62A of a main valve 62 on an arc in the gas flow direction and another valve plate 62A linear, but opposite to the gas flow direction to be led is used, in which a valve plate 62A of a main valve 62 on an arc in the gas flow direction and another valve plate 62A linear, but opposite to the gas flow direction to be led.
- One of the valve plates 62A is in this case on an L-shaped one Lever 19 which is pivotally connected to the rod 13, fixed the lever 19 is pivotable in its center on a stationary wall projection 17 is stored.
- the other valve plate 62A is at the upper end of the rod 13 established.
- the arrangement of the lever 19 and those effective for the gas pressure Surfaces of the valve plate 62A are chosen so that they are on the rod 13 acting forces due to the pressure gradient between the fresh air pressure channel 5 and the junction 1 compensate.
- a circular path and one Linear valve plate guides are also two linear valve plate guides or two circular path
- Figure 5 shows a further embodiment of the invention similar to Figure 3, at which is provided as a main valve, a ball, cone or cylinder valve 63 to to enable the desired pressure compensation.
- FIG. 6 shows a further embodiment of the invention, which attempts to overcome the disadvantages of the embodiment with the piston 80 described with reference to FIG. 2.
- completely mechanically frictionless operation of the piston 80 is not possible, and when the main valve 60 is closed there can still be a connection between the fresh air pressure channel 5 and the mouth 1, so that gas can still flow.
- This can be prevented by replacing the piston 80 with a membrane 81 which has the same or a different effective area or cross section as the piston 80. If the effective area F 81 of diaphragm 81 is different, for example larger, a translation or reduction must be created between diaphragm 81 and rod 13.
- FIG. 1 shows a further embodiment of the invention, which attempts to overcome the disadvantages of the embodiment with the piston 80 described with reference to FIG. 2.
- a lever transmission is provided with a lever arm 21 which is pivotably mounted on one side on a projection of the wall 8 and which can be brought into engagement with the rod 13 on both sides (alternative A) or on one side (alternative B).
- the compensation force which arises due to the pressure drop across the membrane 81, is transmitted to the rod 13 according to the predetermined translation with a compensation arm, which is connected to the membrane 81 on the one hand and pivotably to the lever arm 21 on the other hand.
- the lever arm 21 can only take the rod 13 in the opening direction of the main valve 60, ie there is a one-sided decoupling of the diaphragm 81 from the main valve 60.
- the larger force F 81 xp 3 is thus translated down to the old compensation force of the piston F 80 xp 3 .
- a corresponding embodiment with a lever ratio is also in Versions with pistons are recommended if their effective surfaces deviate from those of the main valve. Leverage kinematics is particularly important for Functional membranes, which can usually only make smaller strokes.
- FIGS. 7 and 8 show further embodiments of the invention.
- the wall 60B supporting the valve seat there is one Membrane 82 provided that the fresh air pressure channel 5 from the junction 1st separates.
- a valve seat of a valve plate 64A of a main valve 64 is shown in FIG the membrane 82 is formed.
- a fulcrum 23 for a lever transmission 24 rigidly connected to the fixed pipes via a star 25.
- the rotatably mounted Lever 27 actuated via rods 28 which, for reasons of gas resistance in the Mouth 1 expediently in the flow direction from the fresh gas channel 2 to the compressor inlet channel 4 in front of and behind the rod 13.
- the Lever mechanism 27 is here because of the risk of contamination and corrosion and for temperature reasons when used as an exhaust gas recirculation device removed from the area to be flushed with exhaust gas.
- the translated compensation force is in turn on the rod 13 on the Transfer valve plate of the main valve 64 and leads to a compensation of the compensating force component.
- FIG. 9 shows a further embodiment of the invention.
- a bellows 84 is provided in the fresh air pressure channel 5, which is attached on one side to a valve disk 65A of a main valve 65 and on its other side, which is opposite in the longitudinal direction, to the upper wall 9 of the fresh air pressure channel 5.
- the valve disk 65A has a passage opening 30, which connects the opening 1 to the interior of the bellows 84 in a gas-permeable manner, as a result of which pressure equalization can develop between the opening 1 and the interior of the bellows 84.
- the bellows 84 contracts in its longitudinal direction, as a result of which a force is exerted on the valve disk 65A in the opening direction of the main valve 65.
- the bellows 84 should be designed so that this force takes over the pressure compensation function.
- Such an embodiment can be advantageous if membranes with sufficient membrane stroke (bellows) are available. For example, lets this results in low friction and no hysteresis achieve; in addition, the bellows 84 can advantageously also act as a closing spring of the main valve 65 act.
- FIG. 1 An embodiment based on this is also possible with a piston 85 instead of a bellows, as shown in FIG.
- a hollow valve body 66A of a main valve 66 connects the opening 1 to the compensation space 10, which receives the piston 85, in a gas-permeable manner, whereby the compensation of the force associated with the pressure drop p 3 -p 2 is possible.
- the piston-specific disadvantages of friction and incomplete tightness occur again in this embodiment.
- FIG. 11 An embodiment according to FIG. 11 can therefore be advantageous, in which the hermetic seal between the fresh air pressure duct 5 and the junction 1 is not produced by a sealing ring 31 on the piston 85 as in FIG. 10, but by an inner valve 32 inside the main valve 67 ,
- the inner valve 32 is opened with a forward stroke of the rod 13, which is caused by the actuating device, in particular by an electric magnet or proportional magnet 14.
- the pressure drop p 5 -p 3 or p 3 -p 2 keeps the inner valve 32 and thus the main valve 67 closed.
- the pressure compensation can be influenced by the choice of the diameter ratio of the effective area of the piston 86 to that of the valve disk 67A and by the ratio of the opening cross sections of the throttle point and the inner valve 32.
- FIG. 12 shows a further embodiment of the gas routing device with pressure compensation Similar to the embodiment shown in Figure 11, with the Difference that here the main valve 68 together with valve plate 68A an inner valve 32 not only by the spring 6, but also is forcibly taken from the rod 13 in the closing direction.
- Figure 13 shows a particularly preferred embodiment of the gas recirculation device with pressure compensation with an inner valve 34, the is opened during the forward stroke of the rod 13.
- the inner valve 34 has here a conical or preferably hemispherical valve disc.
- On in the upper region of the rod 13 attached pin 35 has the task of a Raise the main valve 69 after the preliminary stroke to open the inner valve 34.
- actuating device 14 can optionally also be provided for the actuation of the inner valve
- Internal valve actuating device can be provided that operate independently of main valve and inner valve enabled (not shown).
- the surfaces of the piston should 89 and a guide sleeve 37 can be coordinated (e.g. Steel / bearing metal etc.).
- a protective sleeve or sleeve 36 can optionally be provided, which protects the sliding fit of the piston 89 in the guide sleeve 37 against contamination.
- a cover 38 is designed or provided with a separate filler in order to make a space above the main valve 69, which represents an inner valve compensation space 10 ', as small as possible, so that the desired pressure (p 3 in the closed and p 2 in the open State) is formed as quickly as possible and as little gas as possible can enter this inner valve compensation space 10 '.
- the gas pressure in the inner valve compensation space is denoted by p 10 '.
- a sealing ring 50 which partially seals an opening gap between the piston 89 and the guide sleeve 37, can be used.
- the latter has been chamfered at its lower end on the inside diameter thereof.
- the upper guide of the rod 13 is except through the wall star 40 (Fig. 2, 3rd etc.) or similar devices also through the pin 35, a membrane or a bellows possible.
- exhaust gas recirculation and pressures p 3 > p 5 can result , for example, from a positive purge gradient due to a turbocharger or from mechanical charging of an engine can occur, the valves 60, 64, 65, 66, 67, 68, 69 open, which would lead to loss of charge air.
- One way of counteracting this is to reverse the polarity of the magnet when using a permanent magnet as an armature or a corresponding measure if an electromotive, pneumatic, hydraulic or mechanical actuation of the inner valves is provided as the adjusting device.
- FIGS. 11 to 13 Another possibility in the embodiments shown in FIGS. 11 to 13 is to simply open the inner valve 32 or 34 at such operating points via the magnet or the corresponding actuating device.
- the pressure p 3 which is higher than p 5, would then be present below the main valve 67 to 69 in the mouth 1 and above the piston 86 or 89; so that the main valve 67 to 69 could be closed by, for example, a spring.
- the slight charge air loss via a throttle point between the guide sleeve 11 or 37 and the piston 86 or 89 is manageable.
- FIGS. 14 and 15 show particularly preferred embodiments of the Invention, which differ in essential structural features from those in Fig. 2nd to 13 differentiate embodiments shown. Those constructive Features that correspond to the previous embodiments or similar, are provided with the same reference numerals and a new description is waived in this case.
- valves 34 and 69 can be made of an elastomer. Prefers this can consist of a single component 90 for both valves.
- the outer spring 6 can also be dispensed with.
- the generally higher pressure P 3 is located on the piston 89 via a throttle point 98 and thus also on the valves 34 and 69 and therefore ensures their hermetic tightness.
- the magnet 14 in the preferred embodiment of FIG. 15 only needs the spring 99, the adhesive action of the elastomer, the gas force resulting from the pressure difference (P 3 -P 2 ) x effective area of the inner valve 34 and the mass effects overcome. In order to keep the magnet small, it is advisable to make the cross-section of valve 34 small.
- valve 34 After opening valve 34, because the cross-section of valve 34 is large in each case compared to the cross-section of throttle point 98, a pressure equalization takes place between the space above piston 89 and line 1, so that pressure P 2 prevails in both spaces.
- the main valve 69 can now be opened by the magnet 14 against the spring 99, the adhesive effect in the valve seat of valve 69 and the larger mass effects of the main valve. Forces resulting from pressure differences can no longer be overcome. If the closing command comes, that is to say in the event that P 3 is to be increased compared to P 2 by the loader, the current in the magnet 14 is switched off or even reversed. in the case of current shutdown, spring 99 now has to first close valve 34 and thus also valve 69. This takes place against the residual magnetism and against the mass action of both valves.
- the magnet 14 of the spring 99 could help with the polarity reversal. With appropriate magnetic properties of the armature of magnet 14 could be such Effect will be reinforced.
- valve cross section 69 For primary acoustic reasons it can be indicated for one at first to ensure slow opening of the valve cross section 69, which then in a quick overall opening should pass over. This can be done by current control of the magnet 14 can be reached. But it can also be done by appropriate Design of the diameter ratios of the valve 34 to the valve 69 achieved or be supported. In both cases, a larger or particularly large valve cross section of valve 34, a goal that one to use the smallest possible magnet 14.
- the acoustic goals can in particular also be suitably designed of the valve cross section of valve 69 in the stroke range of the opening phase be, e.g. B. by suitable aerodynamic shaping or by the valve is provided with a suitable throttle collar 97.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Driven Valves (AREA)
- Exhaust-Gas Circulating Devices (AREA)
- Magnetically Actuated Valves (AREA)
Description
- einen Frischluftdruckkanal, der in einen Verdichterausgangskanal eines Verdichters der Ladelufteinrichtung mündet,
- einen frischluftzuführenden Frischluftkanal,
- einen Verdichtereingangskanal und einer in den Frischluftkanal und den Verdichtereingangskanal mündenden Einmündung,
- Figur 1
- eine schematische Darstellung von Teilen eines Frischgas- und des Abgassystems eines Verbrennungsmotors mit einer bevorzugten Anordnung einer erfindungsgemäßen Luftführungseinrichtung b. Die mit dem Bezugszeichen a bezeichnete Einrichtung stellt eine Abgasrückführungseinrichtung dar, welche nicht unter den Schutzbereich der beigefügten Ansprüche fällt;
- Figur 2
- eine schematische Querschnittsdarstellung einer erfindungsgemäßen Luftführungseinrichtung mit einer Druckkompensationsleitung;
- Figur 3
- eine schematische Querschnittsdarstellung einer weiteren Ausführungsform der Erfindung mit einer Drosselklappe als Steuerorgan;
- Figur 4
- eine schematische Querschnittsdarstellung einer weiteren Ausführungsform der Erfindung mit zwei entgegengerichteten Ventilen;
- Figur 5
- eine schematische Querschnittsdarstellung einer weiteren Ausführungsform der Erfindung mit einem Kugel-, Kegel- oder Zylinderventil;
- Figur 6
- eine schematische Querschnittsdarstellung einer weiteren Ausführungsform der Erfindung mit einer Membran und einer Hebelübersetzung;
- Figur 7
- eine schematische Querschnittsdarstellung einer weiteren Ausführungsform der Erfindung mit einer Membran und einer Hebelübersetzung;
- Figur 8
- eine schematische Querschnittsdarstellung einer weiteren Ausführungsform der Erfindung mit einer Membran und einer Hebelübersetzung;
- Figur 9
- eine schematische Querschnittsdarstellung einer weiteren Ausführungsform der Erfindung mit einem Balg;
- Figur 10
- eine schematische Querschnittsdarstellung einer weiteren Ausführungsform der Erfindung mit einem zwecks Druckkompensation über einen hohlen Ventilkörper beaufschlagten Kolben;
- Figur 11
- eine schematische Querschnittsdarstellung einer weiteren Ausführungsform der Erfindung mit einem zusätzlichen inneren Ventil;
- Figur 12
- eine schematische Querschnittsdarstellung einer weiteren Ausführungsform der Erfindung mit einem zusätzlichen inneren Ventil;
- Figur 13
- eine Querschnittsdarstellung einer weiteren Ausführungsform der Erfindung mit einem zusätzlichen inneren Ventil;
- Figur 14
- eine schematische Querschnittsdarstellung einer weiteren bevorzugten Ausführungsform der Erfindung; und
- Figur 15
- eine Querschnittsdarstellung einer weiteren bevorzugten Ausführungsform der Erfindung.
- 1.
- Einmündung
- 2.
- Frischgaskanalbzw. Frischluftkanal
- 3.
- Potentiometer
- 4.
- Verdichtereingangskanal (4b)
- 5.
- Frischluftdruckkanal (5b)
- 6.
- Feder
- 6'.
- Feder
- 8.
- Wand
- 8'.
- Wand
- 9.
- Wand
- 10.
- Kompensationsraum
- 11.
- obere Wand
- 12.
- Kompensationsleitung
- 13.
- Stange
- 14.
- Magnet oder Proportionalmagnet
- 15.
- Hebel
- 17.
- Wandvorsprung
- 19.
- Hebel
- 21.
- Hebelarm
- 23.
- Drehpunkt
- 24.
- Hebelübersetzung
- 25.
- Stern
- 27.
- Hebel
- 28.
- Stangen
- 30.
- Durchlaßöffnung
- 31.
- Dichtungsring
- 32.
- inneres Ventil
- 33.
- inneres Ventil
- 34.
- inneres Ventil
- 35.
- Stift
- 36.
- Schutzhülse
- 37.
- Führungshülse
- 38.
- Deckel
- 40.
- Führungsstern
- 50.
- Dichtungsring
- 60.
- Hauptventil
- 60A.
- Ventilplatte
- 60B.
- Ventilsitz bzw. Wand
- 61.
- Hauptventil
- 61A.
- Drosselklappe
- 62-69.
- Hauptventil
- 62A-69A.
- Ventilplatten
- 80.
- Kolben
- 81-82.
- Membran
- 84.
- Balg
- 85-86.
- Kolben
- 89.
- Kolben
- 90.
- elastische Ventildichtung
- 97.
- Drosselkragen
- 98.
- Drosselstelle
- 99.
- Innere Feder
Claims (10)
- Luftführungseinrichtung für Verbrennungsmotoren mit Ladelufteinrichtung, insbesondere Kraftfahrzeugmotoren, miteinem Frischluftdruckkanal (5b), der in einen Verdichterausgangskanal (108) eines Verdichters (102) der Ladelufteinrichtung mündet,einem frischluftzuführenden Frischluftkanal (2b),einem Verdichtereingangskanal (4b) und einer in den Frischluftkanal (2b) und den Verdichtereingangskanal (4b) mündenden Einmündung (1b),
- Luftführungseinrichtung nach Anspruch 1, wobei eine Seite der Kompensationseinrichtung (80-89) mit dem druckgasseitigen Gasdruck (p3) und die andere Seite mit dem frischgasseitigen Gasdruck (p2) beaufschlagt wird.
- Luftführungseinrichtung nach Anspruch 1 oder 2, wobei die Kompensationseinrichtung (61; 61A; 62; 62A; 63) als eine Drosselklappe, ein Doppel-, Kugel-, Kegel- oder Zylinderventil in dem Steuerorgan (60-69) bereitgestellt ist.
- Luftführungseinrichtung nach Anspruch 1 oder 2, wobei das Steuerorgan (60-69) eine Ventilstange (13) und einen daran festgelegten Ventilteller (60A; 62A-69A) mit einer gasdruckwirksamen Fläche (F3) umfaßt, so daß eine Ventiltellerkraft auf den Ventilteller wirkt, die gleich dem Produkt aus der gasdruckwirksamen Fläche (F3) und der Druckdifferenz (p3 - p2) ist, und die Kompensationseinrichtung zumindest einen Kolben (80; 85; 86; 89), eine Membran (81) und/oder einen Balg (84) umfaßt, welcher an der Ventilstange festgelegt ist und auf dessen gasdruckwirksame Fläche (F3; F80) die Druckdifferenz (p3 - p2) wirkt, so daß eine Kompensationskraft an der Ventilstange (13) angreift, welche die Ventiltellerkraft kompensiert.
- Luftführungseinrichtung nach einem der vorangegangenen Ansprüche, wobei das Steuerorgan (60-69) durch eine mechanische, pneumatische, hydraulische, magnetische oder elektrische Stelleinrichtung (14), insbesondere einen elektrischen Hubmagneten (14), betätigbar ist.
- Luftführungseinrichtung nach einem der vorangegangenen Ansprüche, wobei die Kompensationseinrichtung ein Innenventil (32; 34) umfaßt, welches in dem Steuerorgan bereitgestellt ist.
- Luftführungseinrichtung nach Anspruch 6, wobei ein Gasdruck (p10') in einem Innenventilkompensationsraum (10') über das Innenventil (34) in Verbindung mit einem Öffnungsspalt zwischen einem Kolben (89) der Kompensationseinrichtung (89) und einer Führungshülse (37) des Kolbens (89) steuerbar ist und das Innenventil (34) von einer Stelleinrichtung (14) und/oder einer Innenventilstelleinrichtung betätigbar ist.
- Luftführungseinrichtung nach einem der vorangegangenen Ansprüche, wobei die Kompensationseinrichtung (81;82;83) über eine kinematische Übersetzung, insbesondere eine Hebelübersetzung (21;24), auf das Steuerorgan (60;64) wirkt, um einen Unterschied zwischen für den Gasdruck wirksamen Flächen einerseits des Steuerorgans (60;64) und andererseits der Kompensationseinrichtung (81;82;83) zu kompensieren.
- Luftführungseinrichtung nach einem oder mehreren der vorherigen Ansprüche, wobei das Steuerorgan (60;64;65) durch eine Federwirkung einer Membran (81-83) oder eines Balgs (84) in Schließrichtung vorgespannt ist, wobei insbesondere zusätzlich eine Feder (6, 6') zur Unterstützung der Vorspannung vorgesehen ist.
- Luftführungseinrichtung nach einem oder mehreren der vorherigen Ansprüche, wobei die Kompensationseinrichtung (80-82; 84-86; 89) und das Steuerorgan (60-69) kraftwirksam miteinander verbunden und über die Stelleinrichtung (14) steuerbar sind.
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19904190 | 1999-02-02 | ||
DE19904190 | 1999-02-02 | ||
DE19925242 | 1999-06-02 | ||
DE19925242 | 1999-06-02 | ||
PCT/EP2000/000778 WO2000046533A1 (de) | 1999-02-02 | 2000-02-01 | Gasführungseinrichtung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1149253A1 EP1149253A1 (de) | 2001-10-31 |
EP1149253B1 true EP1149253B1 (de) | 2003-08-27 |
Family
ID=26051640
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP00902645A Expired - Lifetime EP1149253B1 (de) | 1999-02-02 | 2000-02-01 | Gasführungseinrichtung |
Country Status (6)
Country | Link |
---|---|
US (1) | US6557346B1 (de) |
EP (1) | EP1149253B1 (de) |
JP (1) | JP4526709B2 (de) |
DE (1) | DE50003439D1 (de) |
ES (1) | ES2206188T3 (de) |
WO (1) | WO2000046533A1 (de) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6435168B1 (en) * | 2000-02-24 | 2002-08-20 | Delphi Technologies, Inc. | Pressure balancing metering subassembly for use with a modular EGR valve |
LU90685B1 (en) * | 2000-11-28 | 2002-05-29 | Delphi Tech Inc | Exhaust gas recirculation balve for an internal combustion engine |
DE50205356D1 (de) * | 2002-09-23 | 2006-01-26 | Abb Turbo Systems Ag Baden | Verfahren und Vorrichtung zum Betreiben eines Abgasturboladers |
DE10333218A1 (de) * | 2003-07-22 | 2005-02-17 | Robert Bosch Gmbh | (2-flutiges) Ventil mit Absperrklappe zur Steuerung von Gasströmen |
US8302402B2 (en) * | 2008-01-10 | 2012-11-06 | Caterpillar Inc. | Air induction system with recirculation loop |
DE102009049394A1 (de) * | 2009-10-14 | 2011-04-21 | 2G Energietechnik Gmbh | Lastenregelungsvorrichtung und Verfahren zur Lastregelung für einen Motor |
US9567950B2 (en) * | 2010-03-25 | 2017-02-14 | Ford Global Technologies, Llc | Turbocharged engine with naturally aspirated operating mode |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5584817A (en) * | 1978-12-18 | 1980-06-26 | Nissan Motor Co Ltd | Bypass valve for use with exhaust turbocharger of internal-combustion engine |
JPS57178130U (de) * | 1981-05-07 | 1982-11-11 | ||
DE3611869A1 (de) | 1986-04-09 | 1987-10-22 | Ruhrgas Ag | Regler, insbesondere fuer gasmotoren |
JPS63223325A (ja) * | 1987-03-12 | 1988-09-16 | Fuji Heavy Ind Ltd | タ−ボチヤ−ジヤ付エンジンの吸気制御装置 |
US5255659A (en) * | 1992-09-28 | 1993-10-26 | Ford Motor Company | Pressure balanced exhaust gas recirculation valve |
DE4410487C1 (de) * | 1994-03-25 | 1995-03-02 | Daimler Benz Ag | Abgasrückführventil einer Brennkraftmaschine |
DE19639146C1 (de) * | 1996-09-24 | 1997-11-06 | Daimler Benz Ag | Brennkraftmaschine mit Abgasturbolader |
DE19712850A1 (de) * | 1997-03-27 | 1998-10-01 | Bosch Gmbh Robert | Vorrichtung zum Steuern eines Schubumluftventils |
DE19721993A1 (de) * | 1997-05-26 | 1998-12-17 | Ammermann Klaus Dr | Abgasrückführungsventil mit Druckkompensation |
US6293266B1 (en) | 1998-05-26 | 2001-09-25 | A. Kayser Automotive Systems Gmbh | Exhaust gas recirculation device |
DE19833148B4 (de) * | 1998-07-23 | 2005-09-08 | Daimlerchrysler Ag | Verfahren und Vorrichtung zur Funktionsüberprüfung eines druckbeaufschlagten Stellelements in einer Brennkraftmaschine |
-
2000
- 2000-02-01 WO PCT/EP2000/000778 patent/WO2000046533A1/de active IP Right Grant
- 2000-02-01 US US09/889,335 patent/US6557346B1/en not_active Expired - Lifetime
- 2000-02-01 JP JP2000597574A patent/JP4526709B2/ja not_active Expired - Lifetime
- 2000-02-01 DE DE50003439T patent/DE50003439D1/de not_active Expired - Lifetime
- 2000-02-01 EP EP00902645A patent/EP1149253B1/de not_active Expired - Lifetime
- 2000-02-01 ES ES00902645T patent/ES2206188T3/es not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
JP4526709B2 (ja) | 2010-08-18 |
EP1149253A1 (de) | 2001-10-31 |
US6557346B1 (en) | 2003-05-06 |
ES2206188T3 (es) | 2004-05-16 |
DE50003439D1 (de) | 2003-10-02 |
JP2002536585A (ja) | 2002-10-29 |
WO2000046533A1 (de) | 2000-08-10 |
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