EP0985092A1 - Exhaust gas recirculation device - Google Patents
Exhaust gas recirculation deviceInfo
- Publication number
- EP0985092A1 EP0985092A1 EP98925637A EP98925637A EP0985092A1 EP 0985092 A1 EP0985092 A1 EP 0985092A1 EP 98925637 A EP98925637 A EP 98925637A EP 98925637 A EP98925637 A EP 98925637A EP 0985092 A1 EP0985092 A1 EP 0985092A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- exhaust gas
- pressure
- gas
- recirculation device
- pressure plate
- 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
Links
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
- F02M26/67—Pintles; Spindles; Springs; Bearings; Sealings; Connections to actuators
-
- 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
- F02M26/70—Flap valves; Rotary valves; Sliding valves; Resilient valves
Definitions
- the invention relates to an exhaust gas recirculation device with pressure compensation - as described in claim 1.
- Otto and diesel engines are usually provided with exhaust gas recirculation devices, in particular exhaust gas recirculation valves (EGR valves). They partially add exhaust gas to the fresh gas drawn in to reduce NOx emissions, improve fuel consumption and reduce noise.
- EGR valves exhaust gas recirculation valves
- Such exhaust gas recirculation devices include metering or control elements with which the amount of recirculated exhaust gas can be adjusted depending on the operating point. Too little exhaust gas recirculation would miss the desired effects, too large would lead to malfunctions or an undesirable increase in HC or even CO emissions in gasoline engines and in
- control members are generally fully closable valves that are set by a vacuum membrane or a servomotor or a proportional magnet working against a spring, which in turn is controlled by a
- Clock valve or a relay can be operated by the engine control unit.
- the information used for this purpose in the control unit is usually the load and speed of the engine and the amount of air drawn in.
- the feedback of the opening path via a path measuring system is also used.
- the exhaust gas recirculation devices are located between the fluctuating pressure ken in the exhaust system and the fluctuating pressures in the intake system of the engine, the changes in these pressures being accompanied on the one hand by the changes in the operating point and on the other by the intermittent discharge of the exhaust gas and the intermittent intake of the fresh gas.
- An exhaust gas recirculation device for recirculating exhaust gas into a gas supply of engines, in particular motor vehicle engines, comprises an exhaust gas supply, a fresh gas supply and one into the
- Gas supply outlet channel wherein at least the exhaust gas supply and the fresh gas supply are connected to each other via a metering or control member and on the fresh gas supply side of the control member a pressure plate is arranged, the influence of occurring on the exhaust gas and fresh gas side and on affect the exhaust gas flow
- control element which can be formed in particular by a valve or main valve, is in a partially or completely open position
- exhaust gas can flow from the exhaust gas side of the exhaust gas recirculation device in the direction of the fresh gas side.
- the pressure plate is arranged in the gas or exhaust gas flow in the exhaust gas recirculation device in such a way that it forms a flow resistance for the exhaust gas flow flowing around or through it thus, when the exhaust gas flows through from the exhaust gas side towards the fresh gas side, it leads to a partial build-up or an increase in pressure of the exhaust gas flow.
- the gas pressure in a space between the control element and the pressure plate is therefore greater than in a space which is arranged on the fresh gas side of the pressure plate.
- the difference between these gas pressures acting on the pressure plate on the fresh gas and exhaust gas side results in a force acting on the pressure plate.
- This force acting on the pressure plate is used according to the invention to influence or control the position or the free opening cross section of the control member, so that, for example, the free opening cross section of the control member is reduced when one in the direction of the fresh gas side or in the closing direction of the control member directed force on the pressure plate increased.
- the pressure plate can thus be designed in such a way that an increase in the pressure gradient between the exhaust gas side and the fresh gas side of the exhaust gas recirculation device leads to a predetermined reduction in the free opening cross section of the control element and one
- control element is connected to a mechanical, pneumatic, hydraulic, magnetic or electrical actuating device or servomotor.
- a magnet or a proportional magnet has proven to be particularly advantageous since the opening or position of the control member is set very precisely with such a magnet and, above all, it also reacts quickly.
- the exhaust gas recirculation device is provided with a compensation device for the compensation or to compensate for forces that act on the control element from a difference between the exhaust gas side and fresh gas side gas pressure. Due to this compensation device, the pressure drop of the gas pressure via the control member cannot lead to a force component which acts in the direction of an undesired opening or closing of the control member, as a result of which the desired control or regulation of the amount of exhaust gas passed through is considerably improved.
- a second valve plate or piston, diaphragms and / or bellows can serve as the compensation device.
- the compensation device on one side with the exhaust gas pressure, i.e. the gas pressure prevailing in the exhaust gas supply and, on the other hand, the gas pressure on the fresh gas side, i.e. the gas pressure prevailing on the fresh gas side of the control member and thus between the main valve and the pressure plate.
- the exhaust gas pressure i.e. the gas pressure prevailing in the exhaust gas supply
- the gas pressure on the fresh gas side i.e. the gas pressure prevailing on the fresh gas side of the control member and thus between the main valve and the pressure plate.
- Force component which is opposite to the force component to be compensated, has the same amount and thus brings about a compensation of the two force components.
- the compensation device is provided with a kinematic transmission, in particular a lever transmission.
- This translation translates the force component generated by the compensation device to a size that is suitable for compensating the force to be compensated for the control member. This is particularly advantageous if the areas or area contents of the compensation device and control element that are effective for the gas pressures differ.
- the compensation device, the control element and the pressure plate are connected to one another in a force-effective manner and can be controlled via the actuating device.
- Compensation device the pressure plate and forces generated by the actuating device act together on the control element and suitably add or compensate in order to achieve the desired net force or force compo- to exercise tax on the tax body.
- the baffle plate is typically arranged in such a way that the exhaust gas stream flowing out of the control member does not flow directly onto the pressure plate, i.e. that there is no undesired impulse transfer of the inflowing exhaust gas flow to the pressure plate.
- control element is prestressed in the closing direction by a spring action of a membrane or a bellows, wherein in particular a spring can additionally be provided to support the prestress in order to add an additional force component
- the pressure plate can advantageously be arranged and designed such that the gas or exhaust gas essentially flows through precisely defined openings in the pressure plate and as little gas as possible can pass around its outer circumference, i.e. little gas can flow between the pressure plate and a wall adjacent to it, but instead the gas flow is passed through openings designed for it in the pressure plate itself.
- These openings are in particular tuned according to acoustic, fluidic and mechanical aspects.
- an embodiment of the pressure plate is possible, in which it is equipped with additional devices, so that with a small gas pressure gradient or small pressure differences between the gas-side and fresh-gas side gas pressures on the pressure plate, the exhaust gas around the outside
- Circumference of the pressure plate can flow around, but with increasing or larger pressure differences, additional gas passage openings can be opened, through which the gas flow can additionally flow. This will be a Additional and advantageous degree of freedom created for the coordination according to acoustic, fluidic and mechanical aspects.
- An exhaust gas recirculation device is preferred in which a gas pressure in an inner valve compensation chamber is controlled by the interaction of an inner valve with an opening gap between the piston and a guide sleeve of the piston, the inner valve being actuated by the actuating device and / or an additional inner valve actuating device.
- the choice of the diameter of the piston relative to that of the control element, for example the main valve, also influences the tuning of the inner valve to that
- Figure 1 is a schematic cross-sectional view of an inventive
- FIG. 1A shows a schematic cross-sectional illustration of a further embodiment of the invention with an exhaust gas-carrying pressure compensation line and a double valve;
- Figure 2 is a schematic cross-sectional view of another embodiment of the invention with a throttle valve as a control member;
- FIG. 3 shows a schematic cross-sectional representation of a further embodiment of the invention with two opposing valves
- FIG. 4 shows a schematic cross-sectional illustration of a further embodiment of the invention with a ball, cone or cylinder valve
- FIG. 5 shows a schematic cross-sectional representation of a further embodiment of the invention with a membrane and a lever transmission
- FIG. 6 shows a schematic cross-sectional representation of a further embodiment of the invention with a membrane and a lever transmission
- FIG. 7 shows a schematic cross-sectional illustration of a further embodiment of the invention with a membrane and a lever transmission
- Figure 8 is a schematic cross-sectional view of an embodiment of a printing plate
- FIG. 9 shows a schematic cross-sectional illustration of a further embodiment of a printing plate
- Figure 1 0 is a schematic cross-sectional view of another embodiment of the invention with a bellows
- Figure 1 1 is a schematic cross-sectional view of a further embodiment of the invention with a piston acted upon for the purpose of pressure compensation via a hollow valve body;
- Figure 1 2 is a schematic cross-sectional view of a further embodiment of the invention with an additional inner valve
- Figure 1 3 is a schematic cross-sectional view of a further embodiment of the invention with an additional inner valve
- Figure 1 4 is a cross-sectional view of another embodiment of the invention with an additional stationary storage plate
- Figure 1 5 is a cross-sectional view of another embodiment of the invention similar to Figure 12 with an additional pot.
- Figure 1 shows schematically a cross section of a first embodiment of the exhaust gas recirculation device according to the invention.
- the exhaust gas is fed to the exhaust gas recirculation device by means of an exhaust gas duct or exhaust gas supply 5, one side of which opens into the main exhaust gas flow of the engine.
- the exhaust gas supply 5 is connected to a chamber 3 via a valve or main valve 60, which consists of a valve plate 60A and a valve seat or wall 60B.
- the chamber 3 is partially closed by a pressure plate 40, which represents a flow resistance for gas or exhaust gas.
- Gas passage openings (not shown) from the chamber 3 into an opening 1 can be formed between the outer periphery of the pressure plate 40 and a wall 8 or in the pressure plate 40 itself.
- the mouth 1 of the recirculated exhaust gas flow is connected to a fresh gas supply 2 and an outlet channel 4, which carries on the fresh gases mixed with the exhaust gas.
- a compensation chamber or piston chamber 10 for receiving a compensation piston or compensating piston or piston 80 is provided in an upper wall 9 of the exhaust gas supply 5.
- the piston 80 bears on its circumference against a wall or side wall 11 and is connected to an upper part of the wall 11 via a spring or spiral spring 6.
- the piston chamber 1 0 is connected to the chamber 3 via a line or compensating line 1 2 in such a way that the gas pressures in the piston chamber 10 and the chamber 3 can quickly equalize.
- Piston 80, valve plate 60A and pressure plate 40 are connected to one another in this order via a rod 13.
- An actuating device in the form of an electrical magnet or proportional magnet 1 4, via which the main valve 60 can be controlled or regulated, is arranged on a side of the rod 1 3 opposite the piston 80.
- the gas pressure in the mouth 1 of the recirculated exhaust gas flow into the fresh gas is p 3 under operating conditions, the gas pressure p 3 ′ prevails in the chamber 3 between the valve plate 60A and the pressure plate 40, and the gas pressure p 5 is present in the exhaust gas supply 5.
- the gas pressure p 3 ′ prevails in the chamber 3 between the valve plate 60A and the pressure plate 40, and the gas pressure p 5 is present in the exhaust gas supply 5.
- Operating points of a naturally aspirated engine are p 5 > p 3 .
- a positive, ie reverse, purge gradient p 5 ⁇ p 3 may occur when the engine is mechanically or turbocharged.
- the flow resistance connected to the pressure plate 40 leads to an increase in the gas pressure p 3 ′ in the chamber 3 compared to the gas pressure p 3 in the mouth 1 when the main valve 60 is open.
- the exhaust gas will therefore generally flow in the desired direction, ie from the exhaust gas supply 5 in the direction of the junction 1.
- the amount of exhaust gas passed through essentially depends on the opening cross section of the main valve and on the gas pressure gradient across the main valve 60, ie on the pressure difference p 5 -p 3 '.
- the pressure plate 40 serves to minimize the influence of this pressure gradient or this pressure difference p 5 -p 3 or p 5 -p 3 'on the amount of exhaust gas that is passed through.
- a suitable choice of the shape and diameter of the pressure plate 40 and a design of the gas transfer from the Chamber 3 for the mouth 1 between a chamber wall or wall 8 and the outer circumference of the pressure plate 40 and / or through the pressure plate 40 can be achieved that the free opening cross section of the main valve when increasing or decreasing the pressure gradient p 5 - p 3 60, that is to say the opening cross section between the valve plate 60A and the valve seat 60B, is reduced or increased precisely by such an amount that the recirculated exhaust gas quantity does not change with the above pressure fluctuations or changes in the pressure difference and a determinable or predetermined size has or so that the exhaust gas portion in the outlet channel 4 downstream of the mouth ung 1 remains constant and has a determinable or predetermined size.
- the throughput of the recirculated exhaust gas quantity is therefore essentially independent of the fluctuations or variations of fresh and exhaust gas pressure (p 5 and p 3 ) at the exhaust gas recirculation device, ie essentially independent of changes in the gas pressure difference or the pressure drop p 5 - p 3 .
- F 4 is an effective cross-sectional area of the pressure plate 40
- the actuation of the main valve 60 of the exhaust gas recirculation device is preferably achieved essentially by the electrical proportional magnet 1 4 via the rod 1 3, the force being dependent on the proportional magnet 1 4 only on the coil current and not on the position of the armature.
- Such an arrangement has the advantage that it can react quickly and set a valve lift or opening of the valve 60 very precisely.
- FIG. 1A shows a further embodiment of the invention, in which a further possibility of compensating for the force acting in the rod 13 (p 5 -p 3 ') x F 3 is a second valve disk 60A', preferably of slightly larger diameter to be provided as a valve plate 60A in order to precisely compress the force acting on the valve plate 60A.
- This valve plate 60A requires an exhaust gas-carrying, ie sufficiently dimensioned compensation line 1 2A into the room 3.
- valves or main valves which operate in the same or almost the same way and simultaneously or almost simultaneously in the direction of the exhaust gas flow and open in the opposite direction to it.
- FIG. Another embodiment of the invention based on such pressure compensation is shown in FIG. In the simplest way it can be
- FIG. 3 shows a further embodiment of the invention.
- a valve head 62A of a main valve 62 in a circular arc in the exhaust gas flow direction, and another valve disc 62 linear, but opposite to the exhaust gas is guided ⁇ flow direction.
- One of the valve plates 62A is in this case fixed to an L-shaped lever 1 9, which is pivotally connected to the rod 1 3, the lever 1 9 being pivotally mounted in its center on a stationary wall projection 1 7.
- the other valve plate 62A is at the upper end of the
- Pole 1 3 set.
- the arrangement of the lever 1 9 and the effective areas of the valve plate 62A for the gas pressure are chosen so that the forces acting on the rod 1 3 due to the pressure gradient between the Compensate exhaust gas supply 5 and chamber 3.
- two linear valve plate guides or two circular path guides are also possible.
- FIG. 4 shows a further embodiment of the invention similar to FIG. 2, in which a ball, cone or cylinder valve 63 is provided as the main valve in order to enable the desired pressure compensation.
- FIG. 5 shows a further embodiment of the invention, which seeks to overcome the disadvantages of the embodiment with the piston 80 described with reference to FIG. 1.
- completely mechanically frictionless operation of the piston 80 is not possible and, with the main valve 60 closed, there can still be a connection between the exhaust gas supply 5 and the mouth 1, so that exhaust gas can still flow to the intake side of the engine. This can be prevented by the
- Piston 80 is replaced by a membrane 81 which has the same or a different effective area or cross section as piston 80. If the effective area F 81 of membrane 81 is different, for example larger, a translation or reduction must be created between membrane 81 and rod 13.
- a lever transmission with a lever arm 21 which is pivotally 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 that arises due to the pressure drop across the membrane 81 is with a compensation arm that with the membrane 81 on the one hand and pivotable with the
- Lever arm 21 is connected on the other hand, transferred to the rod 1 3 according to the predetermined translation.
- 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 5 is translated down to the old compensation force of the piston F 80 xp 5 .
- a corresponding embodiment with a lever ratio is also in Versions with pistons are recommended if their effective areas differ from those of the main valve.
- Lever kinematics are particularly useful for diaphragms, which can generally only make smaller strokes.
- Figures 6 and 7 show further embodiments of the invention.
- an embodiment is proposed which does not require the line 1 2 of the embodiment described with reference to FIG. 1.
- a membrane 82 is provided here, which separates the exhaust gas supply 5 from the chamber 3.
- a valve seat of a valve plate 64A of a main valve 64 is hereby formed in the membrane 82.
- a fulcrum 23 for a lever transmission 24 is rigidly connected to the stationary pipes via a star 25.
- the junction 1 expediently lies in the flow direction from the fresh gas supply 2 to the outlet channel 4 in front of and behind the rod 13.
- the lever mechanism 27 is located here because of the contamination and corrosion ⁇ danger and temperature reasons from the area, which is flushed by exhaust gas.
- the translated compensation force is in turn over the bar
- FIG. 8 shows an expedient embodiment of the hollow pressure plate or of the pressure body 41, for the one described with reference to FIGS. 6 and 7
- Embodiments are provided. For acoustic, mechanical and fluidic reasons, it can be advantageous that as little exhaust gas as possible around the outer edge or outer circumference of this pressure element 41 passes around, but mainly through the flow openings or gas passage openings 29 provided for this purpose, which can be designed like a nozzle.
- FIG. 9 shows that the wall 8 'surrounding the pressure plate 42 can also be shaped differently than purely cylindrical for reasons of coordination.
- Figure 1 0 shows a further embodiment of the invention.
- a bellows 84 is provided in the exhaust gas supply 5, which is attached on one side to a valve plate 65A of a main valve 65 and on its other side opposite in the longitudinal direction on the upper wall 9 of the exhaust gas supply 5.
- the valve plate 65A has a passage opening 30, which connects the chamber 3 to the interior of the bellows 84 in a gas-permeable manner, as a result of which pressure equalization can form between the chamber 3 and the interior of the bellows 84. If the pressure drop p 5 -p 3 'increases, the pressure increases
- Bellows 84 together in its longitudinal direction, thereby exerting a force in the opening direction of the main valve 65 on the valve plate 65A.
- 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 a sufficient membrane stroke (bellows) are available. For example, low friction and no hysteresis can be achieved in this way; in addition, the bellows 84 can advantageously simultaneously act as a closing spring of the main valve 65.
- FIG. 11 An embodiment based on this is also possible with a piston 85 instead of a bellows, as shown in FIG. 11.
- a hollow valve body 66A of a main valve 66 connects the chamber 3 in a gas-permeable manner to the compensation space 10 , which receives the piston 85, whereby the force associated with the pressure drop p 5 -p 3 'can be compensated.
- the piston-specific disadvantages of friction and incomplete tightness occur again.
- An embodiment according to FIG. 1 2 can therefore be advantageous, in which the hermetic seal between the exhaust gas supply 5 and the mouth 1 is not provided by a sealing ring 31 on the piston 85 as in FIG. 1 1, but by an inner valve 32 inside the main valve 67 will be produced.
- the inner valve 32 is opened with a forward stroke of the rod 1 3, which is caused by the actuating device, in particular by an electric magnet or proportional magnet 14. As long as the inner valve 32 is closed, the pressure drop p 5 -p 3 keeps the inner valve 32 and thus the main valve 67 closed. If the inner valve 32 is opened by the preliminary stroke, a throttling point results between the outer circumference of the valve
- 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 plate 67A and by the ratio of the opening cross sections of the throttle point and the inner valve 32.
- Figure 1 3 shows a further embodiment of the exhaust gas recirculation device with pressure compensation similar to the embodiment shown in Figure 1 2, with the difference that here the main valve 68 with valve plate 68A together with an inner valve 32 not only by the spring 6, but also forcibly by the rod 1 3 is taken in the closing direction.
- Figure 1 4 shows a particularly preferred embodiment of the exhaust gas recirculation device with pressure compensation with an inner valve 34 which is opened during the forward stroke of the rod 1 3.
- the inner valve 34 has a conical or preferably hemispherical valve disk.
- a pin 35 fastened to the upper area of the rod 13 has the task of lifting a main valve 69 after the preliminary stroke to open the inner valve 34.
- an inner valve actuating device provided specifically for actuating the inner valve can also be provided, which independently 1 7
- the tongues 55 are fixed on one side of the pressure plate 44. A further refinement of the tuning is possible through the number of openings 29 'and through the choice of the diameter of the gas passage openings 29'.
- gas passage openings 29 ' are chosen to be sufficiently large from the outset and are closed with a spring-loaded plate or sealing plate 56 which seals at their edges, as shown in the embodiment shown in FIG.
- the sealing plate 56 opens more or less into a pot 58 surrounding it, whereby it opens up elongated openings or passages 59, the opening characteristics of which are to be determined during the tuning. As long as they remain constant, the shape of such passages can even be used to implement any force-throughput characteristics.
- pressures p 3 > p 5 which can occur, for example, in the event of a positive purge gradient due to a turbocharger or when a motor is mechanically charged, yourself
- Open valves 60, 64, 65, 66, 67, 68, 69 which would lead to loss of charge air.
- One way to counteract 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 actuating device.
- FIG. 1 2 Another possibility in the embodiments shown in FIG. 1 2 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 chamber 3 and above the piston 86 or 89, so that the main valve 67 to 69 are closed by a spring, for example 1 6 of main valve and inner valve enabled (not shown).
- a protective sleeve or sleeve 36 can optionally be provided, which protects the sliding fit of the piston 89 in a guide sleeve 37 against contamination.
- a cover 38 is designed or provided with a separate filler piece 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 5 in the closed and p 3 'in the open state) is formed as quickly as possible and as little exhaust 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. In order to facilitate the threading of the piston 89 into the guide sleeve 37, this has at its lower
- a baffle plate 52 is provided to eliminate the distorting effect of the back pressure of the gases flowing from the opening cross section of the main valve 69 on a pressure plate 44, i.e. it is to be prevented that the exhaust gas stream flowing through the main valve from the exhaust gas supply 5 in the direction of the junction 1 flows directly onto the pressure plate 44, since this causes an undesired impulse transmission with a distorting effect on the control or.
- Control properties of the exhaust gas recirculation device can have. It has proven to be particularly advantageous to pull a collar 53 of the storage plate 52 into the main valve 69 as high as possible.
- the storage plate 52 can advantageously take over the upper guidance of the rod 13 at the same time. Such upper guidance of the rod 1 3 is also possible through the pressure plate 44, the pin 35, a membrane or a bellows.
- openings or gas passage openings 29 'in the pressure plate 44 are spring-loaded valves.
- FIG. 1 4 Such an embodiment is shown in FIG. 1 4, in which the gas passage openings 29 'are covered by resilient tongues 55 of different spring stiffness. could.
- the slight charge air loss via a throttle point between the guide sleeve 1 1 or 37 and piston 86 or 89 is manageable.
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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)
- Fluid-Driven Valves (AREA)
- Processing Of Solid Wastes (AREA)
- Treating Waste Gases (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19721993A DE19721993A1 (en) | 1997-05-26 | 1997-05-26 | Exhaust gas recirculation valve with pressure compensation |
DE19721993 | 1997-05-26 | ||
PCT/EP1998/003092 WO1998054460A1 (en) | 1997-05-26 | 1998-05-26 | Exhaust gas recirculation device |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0985092A1 true EP0985092A1 (en) | 2000-03-15 |
EP0985092B1 EP0985092B1 (en) | 2002-08-14 |
Family
ID=7830537
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98925637A Expired - Lifetime EP0985092B1 (en) | 1997-05-26 | 1998-05-26 | Exhaust gas recirculation device |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP0985092B1 (en) |
AT (1) | ATE222324T1 (en) |
DE (2) | DE19721993A1 (en) |
ES (1) | ES2178837T3 (en) |
WO (1) | WO1998054460A1 (en) |
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JP4526709B2 (en) * | 1999-02-02 | 2010-08-18 | アー. カイザー アウトモティーフェ ジステームス ゲゼルシャフト ミット ベシュレンクテル ハフツング | Gas transport equipment |
DE19920820A1 (en) * | 1999-05-06 | 2000-11-09 | Bosch Gmbh Robert | Valve for exhaust gas recycling in IC engine has pressure equalising ducts through the valve element between the outlet and the inside of a bellows attachment to the valve |
DE19936657A1 (en) * | 1999-08-04 | 2001-02-15 | Mannesmann Vdo Ag | Control valve |
US6604542B1 (en) * | 2000-02-24 | 2003-08-12 | Delphi Technologies, Inc. | Modular exhaust gas recirculation valve |
US6435168B1 (en) * | 2000-02-24 | 2002-08-20 | Delphi Technologies, Inc. | Pressure balancing metering subassembly for use with a modular EGR valve |
ES2243583T3 (en) | 2000-12-22 | 2005-12-01 | A. Kayser Automotive Systems Gmbh | RECIRCULATION VALVE OF EXHAUST GASES WITH REGULATING PLATE OF THE PIVOTING MOUNTED PRESSURE. |
DE10333218A1 (en) * | 2003-07-22 | 2005-02-17 | Robert Bosch Gmbh | (2-valve) valve with shut-off valve for controlling gas flows |
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JPS57203859A (en) * | 1981-06-09 | 1982-12-14 | Nippon Denso Co Ltd | Fuel atomization control device for internal-combustion engine |
US5163295A (en) * | 1991-09-09 | 1992-11-17 | Eaton Corporation | Controlling exhaust gas recirculation in a pressure boosted internal combustion engine |
JPH06147025A (en) * | 1992-11-11 | 1994-05-27 | Toyota Motor Corp | Exhaust reflux device |
DE4334370C1 (en) * | 1993-10-08 | 1994-09-01 | Daimler Benz Ag | Exhaust valve of an internal combustion engine |
-
1997
- 1997-05-26 DE DE19721993A patent/DE19721993A1/en not_active Withdrawn
-
1998
- 1998-05-26 AT AT98925637T patent/ATE222324T1/en not_active IP Right Cessation
- 1998-05-26 WO PCT/EP1998/003092 patent/WO1998054460A1/en active IP Right Grant
- 1998-05-26 DE DE59805195T patent/DE59805195D1/en not_active Expired - Lifetime
- 1998-05-26 EP EP98925637A patent/EP0985092B1/en not_active Expired - Lifetime
- 1998-05-26 ES ES98925637T patent/ES2178837T3/en not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO9854460A1 * |
Also Published As
Publication number | Publication date |
---|---|
ATE222324T1 (en) | 2002-08-15 |
EP0985092B1 (en) | 2002-08-14 |
ES2178837T3 (en) | 2003-01-01 |
DE59805195D1 (en) | 2002-09-19 |
DE19721993A1 (en) | 1998-12-17 |
WO1998054460A1 (en) | 1998-12-03 |
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