US20080087739A1 - Methods and apparatus for injecting atomized fluid - Google Patents
Methods and apparatus for injecting atomized fluid Download PDFInfo
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- US20080087739A1 US20080087739A1 US11/714,718 US71471807A US2008087739A1 US 20080087739 A1 US20080087739 A1 US 20080087739A1 US 71471807 A US71471807 A US 71471807A US 2008087739 A1 US2008087739 A1 US 2008087739A1
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- reagent
- whirl
- injector
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- injector body
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
- F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
- F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
- F01N3/18—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by methods of operation; Control
- F01N3/20—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by methods of operation; Control specially adapted for catalytic conversion ; Methods of operation or control of catalytic converters
- F01N3/2066—Selective catalytic reduction [SCR]
- F01N3/208—Control of selective catalytic reduction [SCR], e.g. dosing of reducing agent
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
- F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
- F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
- F01N3/18—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by methods of operation; Control
- F01N3/20—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by methods of operation; Control specially adapted for catalytic conversion ; Methods of operation or control of catalytic converters
- F01N3/2066—Selective catalytic reduction [SCR]
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2560/00—Exhaust systems with means for detecting or measuring exhaust gas components or characteristics
- F01N2560/02—Exhaust systems with means for detecting or measuring exhaust gas components or characteristics the means being an exhaust gas sensor
- F01N2560/026—Exhaust systems with means for detecting or measuring exhaust gas components or characteristics the means being an exhaust gas sensor for measuring or detecting NOx
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2560/00—Exhaust systems with means for detecting or measuring exhaust gas components or characteristics
- F01N2560/06—Exhaust systems with means for detecting or measuring exhaust gas components or characteristics the means being a temperature sensor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2560/00—Exhaust systems with means for detecting or measuring exhaust gas components or characteristics
- F01N2560/07—Exhaust systems with means for detecting or measuring exhaust gas components or characteristics the means being an exhaust gas flow rate or velocity meter or sensor, intake flow meters only when exclusively used to determine exhaust gas parameters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2610/00—Adding substances to exhaust gases
- F01N2610/02—Adding substances to exhaust gases the substance being ammonia or urea
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2610/00—Adding substances to exhaust gases
- F01N2610/03—Adding substances to exhaust gases the substance being hydrocarbons, e.g. engine fuel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2610/00—Adding substances to exhaust gases
- F01N2610/11—Adding substances to exhaust gases the substance or part of the dosing system being cooled
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2610/00—Adding substances to exhaust gases
- F01N2610/14—Arrangements for the supply of substances, e.g. conduits
- F01N2610/1453—Sprayers or atomisers; Arrangement thereof in the exhaust apparatus
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2610/00—Adding substances to exhaust gases
- F01N2610/14—Arrangements for the supply of substances, e.g. conduits
- F01N2610/1453—Sprayers or atomisers; Arrangement thereof in the exhaust apparatus
- F01N2610/146—Control thereof, e.g. control of injectors or injection valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2900/00—Details of electrical control or of the monitoring of the exhaust gas treating apparatus
- F01N2900/06—Parameters used for exhaust control or diagnosing
- F01N2900/08—Parameters used for exhaust control or diagnosing said parameters being related to the engine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2900/00—Details of electrical control or of the monitoring of the exhaust gas treating apparatus
- F01N2900/06—Parameters used for exhaust control or diagnosing
- F01N2900/18—Parameters used for exhaust control or diagnosing said parameters being related to the system for adding a substance into the exhaust
- F01N2900/1806—Properties of reducing agent or dosing system
- F01N2900/1808—Pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2900/00—Details of electrical control or of the monitoring of the exhaust gas treating apparatus
- F01N2900/06—Parameters used for exhaust control or diagnosing
- F01N2900/18—Parameters used for exhaust control or diagnosing said parameters being related to the system for adding a substance into the exhaust
- F01N2900/1806—Properties of reducing agent or dosing system
- F01N2900/1811—Temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2900/00—Details of electrical control or of the monitoring of the exhaust gas treating apparatus
- F01N2900/06—Parameters used for exhaust control or diagnosing
- F01N2900/18—Parameters used for exhaust control or diagnosing said parameters being related to the system for adding a substance into the exhaust
- F01N2900/1806—Properties of reducing agent or dosing system
- F01N2900/1814—Tank level
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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
- F02M53/00—Fuel-injection apparatus characterised by having heating, cooling or thermally-insulating means
- F02M53/04—Injectors with heating, cooling, or thermally-insulating means
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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
- F02M53/00—Fuel-injection apparatus characterised by having heating, cooling or thermally-insulating means
- F02M53/04—Injectors with heating, cooling, or thermally-insulating means
- F02M53/08—Injectors with heating, cooling, or thermally-insulating means with air cooling
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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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/162—Means to impart a whirling motion to fuel upstream or near discharging orifices
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present invention relates generally to the reduction of emissions produced by lean burn engines.
- the present invention provides methods and apparatus for injecting fluid, such as an aqueous urea solution, into an exhaust stream in order to reduce oxides of nitrogen (NOx) emissions from diesel engine exhaust.
- fluid such as an aqueous urea solution
- Lean burn engines provide improved fuel efficiency by operating with an excess of oxygen over the amount necessary for complete combustion of the fuel. Such engines are said to run “lean” or on a “lean mixture.” However, this increase in fuel economy is offset by undesired pollution emissions, specifically in the form of oxides of nitrogen (NOx).
- NOx oxides of nitrogen
- SCR selective catalytic reduction
- SCR when used, for example, to reduce NOx emissions from a diesel engine, involves injecting an atomized reagent into the exhaust stream of the engine in relation to one or more selected engine operational parameters, such as exhaust gas temperature, engine rpm or engine load as measured by engine fuel flow, turbo boost pressure or exhaust NOx mass flow.
- the reagent/exhaust gas mixture is passed through a reactor containing a catalyst, such as, for example, activated carbon, or metals, such as platinum, vanadium or tungsten, which are capable of reducing the NOx concentration in the presence of the reagent.
- a catalyst such as, for example, activated carbon, or metals, such as platinum, vanadium or tungsten
- aqueous urea solution is known to be an effective reagent in SCR systems for diesel engines.
- use of such an aqueous urea solution involves many disadvantages.
- Urea is highly corrosive and attacks mechanical components of the SCR system, such as the injectors used to inject the urea mixture into the exhaust gas stream.
- Urea also tends to solidify upon prolonged exposure to high temperatures, such as encountered in diesel exhaust systems. Solidified urea will accumulate in the narrow passageways and exit orifice openings typically found in injectors. Solidified urea may foul moving parts of the injector and clog any openings, rendering the injector unusable.
- urea deposits will form in the catalytic reactor, inhibiting the action of the catalyst and thereby reducing the SCR system effectiveness.
- High injection pressures are one way of minimizing the problem of insufficient atomization of the urea mixture.
- high injection pressures often result in over-penetration of the injector spray plume into the exhaust stream, causing the plume to impinge on the inner surface of the exhaust pipe opposite the injector. Over-penetration leads to inefficient use of the urea mixture and reduces the range over which the vehicle can operate with reduced NOx emissions. Only a finite amount of aqueous urea can be carried on a vehicle, and what is carried should be used efficiently to maximize vehicle range and reduce the need for frequent fill ups of the reagent.
- aqueous urea is a poor lubricant. This characteristic adversely affects moving parts within the injector and requires that special fits, clearances and tolerances be employed between relatively moving parts within an injector. Aqueous urea also has a high propensity for leakage. This characteristic adversely affects mating surfaces requiring enhanced sealing resources in many locations.
- the present invention provides improved methods and apparatus for injecting fluid, such as an aqueous urea solution, into an exhaust stream in order to reduce oxides of nitrogen (NOx) emissions from diesel engine exhaust.
- fluid such as an aqueous urea solution
- the injector of the present invention is an enhanced performance atomizer for use with any diesel or natural gas engine.
- the present invention provides improvements to prior art aqueous urea injectors, in particular, improvements to an aqueous urea injector of the type described in the '603 patent.
- the present invention utilizes atomization techniques that occur internal to the injector.
- the present invention uses mechanical spill return atomization techniques to produce droplets smaller than anticipated by the inventors, in particular, droplets approximately 50 ⁇ m SMD (Sauter mean diameter) or smaller. This size range is appropriate to allow urea to react into ammonia within the residence time associated with an on-road diesel engine, unlike the injector described in the '603 patent.
- This effect is achieved through the use of a whirl plate having a plurality of whirl slots surrounding the exit orifice of the injector, which produce a high velocity rotating flow in the whirl chamber.
- the present invention provides further improvements over the injector of the '603 patent, including increased magnetic pull strength of the metering plug over a wide temperature range, prolonged life of the injector valve and associated actuating components, and cooling with the urea throughout the injector. Additionally, the present invention incorporates adjustable spray quality characteristics on line, and interchangeability of orifice plates for multiple size applications.
- the ribbed injector body provides additional cooling capability.
- the present invention may be further adapted to provide an injector for injecting hydrocarbons particularly for the purposes of regenerating a particulate filter in a diesel exhaust or for use in a hydrocarbon based lean-NOx catalyst system.
- the combination of pulse width modulation providing instantaneous timing control and mechanical atomization techniques is appropriate for providing small quantities of hydrocarbons with precise timing.
- the cooling aspects provided by the present invention allow the injector to survive the hot exhaust conditions as well as prevent pre-ignition of the hydrocarbon.
- An injector which comprises an injector body, and a whirl chamber arranged on the injector body.
- the whirl chamber has an exit orifice.
- a plurality of whirl slots may be provided in the whirl chamber for imparting a rotational velocity to fluid introduced into the whirl chamber.
- a valve seat positioned within the whirl chamber surrounds the exit orifice.
- a metering plug may be arranged within the injector body.
- An actuator may also be mounted on the injector body and connected to the metering plug for moving the metering plug between closed and open positions. The actuator may be located in the injector body and connected to the metering plug for enabling movement of the metering plug from the closed position to the open position.
- the metering plug may be located in the injector body such that when the metering plug is in a closed position, the metering plug is seated in the valve seat preventing fluid from being dispensed from the exit orifice.
- the fluid may be circulated through the injector to cool the injector when the metering plug is in the closed position.
- the metering plug is removed from the valve seat allowing fluid to be dispensed from the exit orifice.
- the injector may further comprise a fluid inlet extending into the injector and a fluid outlet extending out of the injector.
- the fluid inlet and fluid outlet may communicate with the whirl chamber via a hollow portion of the metering plug.
- the fluid inlet, the fluid outlet, and the hollow portion of the metering plug may provide a flow path for fluid through the injector, thereby enabling cooling of the injector.
- the flow path for the fluid through the injector may be provided independently of the position of the metering plug.
- a metering orifice located in the injector body may control the flow rate of cooling fluid flowing through the injector at a given inlet pressure.
- the fluid may be a urea solution or a hydrocarbon.
- a plurality of ribs, surrounding the injector body may be provided to disperse heat away from the injector body.
- a heat shield, surrounding the exit orifice, may also be provided to decrease the heat transfer from the exhaust stream to the injector body.
- the heat shield may have an aperture therethrough aligned with the exit orifice, thereby allowing fluid released from the whirl chamber to pass through the heat shield.
- the heat shield may comprise a plate surrounding the exit orifice and a layer of insulating material arranged on the plate.
- the injector body and metering plug may comprise stainless steel.
- a biasing member may be provided to bias the metering plug into the closed position, thereby providing a fail-closed valve.
- the biasing member may be a coil spring arranged coaxially with the metering plug.
- the actuator may comprise a magnetic coil generating a magnetic force.
- the magnetic force may effect a sliding motion of the metering plug against the biasing member when the magnetic coil is energized.
- the metering plug may thereby be moved from the closed position to the open position within the whirl chamber when the actuator is energized, enabling fluid to be dispensed from the exit orifice of the whirl chamber.
- Means for energizing the magnetic coil may be provided. For example, a 12 V pulse width modulated signal may energize the magnetic coil for a definite time period to inject a certain amount of fluid. Other means for energizing the magnetic coil which will be apparent to those skilled in the art may also be employed.
- a method of injecting a fluid into a gas stream is also provided in accordance with the invention.
- One example embodiment of such a method includes introducing a reagent into an injector body via a fluid inlet, providing a predetermined pressure setpoint for pressurizing the reagent in the injector body, imparting a high velocity rotating flow to at least a portion of the pressurized reagent within a whirl chamber of the injector body, and metering a precise amount of atomized reagent from an exit orifice into the exhaust gas stream.
- the predetermined pressure setpoint may be variable within a range of approximately 50 to 200 pounds per square inch.
- the whirl chamber may have a plurality of whirl slots.
- a fluid outlet may be provided for removing any reagent not metered into the exhaust stream from the injector body.
- the fluid in excess of the amount precisely metered may be circulated through the injector body to enable at least one of: (a) maintaining of the reagent within a desired temperature range; and (b) maintaining of the injector within a desired temperature range.
- a flow rate of the reagent circulating through the injector body may be variable from approximately 2 to 20 gallons per hour.
- the desired temperature range for the reagent may comprise 5° C. to 85° C.
- the reagent may comprise a urea solution, a hydrocarbon based reagent, or any other suitable reagent capable of reducing unwanted substances from engine exhaust streams.
- the exhaust gas stream may comprise a diesel engine exhaust stream or a natural gas or biodiesel engine exhaust stream.
- the predetermined pressure setpoint may be variable to provide at least one of increased operating range and varied spray patterns. Varying the predetermined pressure setpoint may vary an average droplet size of the atomized reagent metered into the exhaust gas stream. The average droplet size may be within a range of approximately 40 to 60 ⁇ m SMD.
- Varying the predetermined pressure setpoint may also vary a flow rate of the atomized reagent metered into the exhaust gas stream.
- the flow rate of the atomized reagent metered into the exhaust gas stream may be varied from approximately 0.5 to approximately 700 grams per minute (e.g., by varying at least one of the predetermined pressure, injector on-time, pulse width modulation frequency of the injector, and exit orifice size). Varying the flow rate further varies at least one of: (1) a droplet size of the atomized reagent metered into the exhaust gas stream; and (2) an amount of cooling provided by circulating reagent remaining in the injector body through the injector body.
- the plurality of whirl slots may comprise at least four whirl slots.
- the whirl slots may be arranged transversely to a longitudinal axis of the injector body.
- the whirl chamber may be provided in a whirl plate, which may be removable from the injector body.
- different whirl plates with correspondingly different characteristics can be interchanged in the injector body for different applications of the injector (e.g., different whirl plates to provide certain performance characteristics for passenger cars, light duty trucks, heavy duty trucks, generators, and the like).
- the different whirl plates may provide different spray patterns of the atomized reagent metered into the exhaust gas stream.
- the different characteristics of the different whirl plates may comprise at least one of a different number of whirl slots, whirl slots of different length, whirl slots of different width, whirl slots of different depth, a differently sized whirl chamber, a differently sized exit orifice, and the like.
- a metering plug may be arranged within a lower section of the injector body. The metering of the reagent into the exhaust gas stream may be controlled via movement of the metering plug from between an open position opening the exit orifice and a closed position closing the exit orifice.
- a flow path may be provided for the reagent through the injector body.
- the flow path may comprise a fluid inlet arranged in the lower section of the injector body, a hollow portion extending through the metering plug, and a fluid outlet in an upper section of the injector body.
- the reagent may be continuously circulated through the flow path, thereby enabling continuous cooling of the injector in both the open and closed position of the metering plug.
- the fluid inlet may be proximate the whirl chamber in a lower portion of the injector body and the fluid outlet may be positioned in a top portion of the injector body. Cooling of the injector tip (e.g., in the region of the valve seat) is of great importance to prevent solidification of the reagent in this area, which can result in clogging of the injector. By positioning the fluid inlet adjacent the whirl chamber in the lower portion of the injector body, cooling at the injector tip is maximized since the fluid is not significantly heated by traveling through the injector body.
- FIG. 1 shows a schematic diagram of an example embodiment of an on-road diesel engine with a pollution emission control system using an injector according to the present invention
- FIG. 2 shows a longitudinal cross-sectional view of an example embodiment of an injector according to the invention
- FIG. 3 shows top, cross-sectional, and bottom views of an example embodiment of a whirl plate in accordance with the present invention
- FIG. 4 ( FIGS. 4A and 4B ) shows an example embodiment of a metering plug used in the injector of FIG. 2 ;
- FIG. 5 shows a perspective view of an example embodiment of an injector mounted on an exhaust tube in accordance with the present invention.
- FIG. 1 shows an example pollution control system for reducing NOx emissions from the exhaust of a diesel engine 21 .
- solid lines between the elements of the system denote fluid lines and dashed lines denote electrical connections.
- the system of the present invention may include reagent tank 10 for holding the reagent (e.g., aqueous urea) and a delivery module 12 for delivering the reagent from the tank 10 .
- the tank 10 and delivery module 12 may form an integrated reagent tank/delivery module.
- an electronic injection control unit 14 is also provided as part of the system.
- an injector module 16 and an exhaust system 19 having at least one catalyst bed 17 .
- the delivery module 12 may comprise a pump that is supplied reagent from the tank 10 through an in-line filter 23 via a supply line 9 .
- the reagent tank 10 may be polypropylene, epoxy coated carbon steel, PVC, or stainless steel and sized according to the application (e.g., vehicle size, intended use of the vehicle, and the like).
- the filter 23 may include a housing constructed of rigid plastic or stainless steel with a removable cartridge.
- a pressure regulator (not shown) may be provided to maintain the system at predetermined pressure setpoint (e.g., approximately 50-200 psi) and may be located in the return line 35 from the injector 16 .
- a pressure sensor may be provided in the flexible line leading to the reagent injector 16 .
- the system may also incorporate various freeze protection strategies to unthaw frozen urea or to prevent the urea from freezing.
- reagent is circulated continuously between the tank 10 and the injector 16 to cool the injector and minimize the dwell time of the reagent in the injector so that the reagent remains cool.
- Continuous reagent circulation is necessary for temperature-sensitive reagents, such as aqueous urea, which tend to solidify upon exposure to elevated temperatures of 300° C. to 650° C. as would be experienced in an engine exhaust system. It has been found to be important to keep the urea mixture below 140° C. and preferably in a lower operating range between 5° C.
- the amount of reagent required may vary with load, engine RPM, engine speed, exhaust gas temperature, exhaust gas flow, engine fuel injection timing, and desired NOx reduction. All or some of the engine operating parameters may be supplied from the engine control unit 27 via the engine/vehicle databus to the reagent injection controller 14 .
- the reagent injection control unit 14 could also be included as part of the engine control unit 27 if the truck manufacturer agrees to provide that functionality.
- Exhaust gas temperature, exhaust gas flow and exhaust back pressure may be measured by respective sensors.
- a minimum reagent level switch or programmed logic based on voltage may be used to prevent the injection system from running dry and overheating. Once a minimum reagent level in the tank 10 is reached, injection will cease and a fault light and/or a text alarm will illuminate in the cab of the vehicle.
- the injection rate may be set by programming the reagent injection control unit 14 with an injection control strategy or map, as described in commonly owned co-pending U.S. Pat. No. 6,941,746 issued on Sep. 13, 2005 entitled “Mobile Diesel Selective Catalytic Reduction Systems and Methods” which is incorporated herein and made a part hereof by reference.
- the injection strategy may be developed by temporarily installing a NOx detector 25 on the vehicle.
- the NOx detector 25 may be a sensor or a meter with a sampling system.
- FIG. 1 shows a NOx meter 25 which analyzes the gas concentration or mass at a location external to the exhaust system 19 .
- FIG. 2 shows a cross-sectional view of an example embodiment of the injector 16 according to the present invention, which may be used in the system shown in FIG. 1 .
- Injector 16 may comprise an injector body 18 having an upper section 18 a and a lower section 18 b.
- An elongated cylindrical chamber 30 may be disposed within the injector body 18 .
- the chamber 30 may be in fluid communication with a whirl plate 50 , which has an exit orifice 22 that opens onto the exhaust gases within the exhaust system 19 ( FIG. 1 ) of a diesel engine when mounted thereon.
- Surrounding exit orifice 22 may be a valve seat 24 which can have any practical shape but is preferably conical.
- a valve member in the form of an elongated metering plug 26 may be slidably mounted within the chamber 30 .
- FIG. 3A shows a top view of the whirl plate 50 .
- FIG. 3B shows a cross-sectional view of the whirl plate 50 .
- FIG. 3C shows a bottom view of the whirl plate 50 .
- the whirl plate 50 may include a plurality of whirl slots 51 surrounding the valve seat 24 and forming a whirl chamber 52 in the area surrounding the end 28 of the metering plug 26 (see FIG. 2 ).
- the whirl slots 51 may be arranged transversely to a longitudinal axis of the injector body 18 , as shown in FIG. 3A .
- valve seat 24 surrounds the exit orifice 22 for dispensing the atomized fluid from the whirl chamber 52 .
- the whirl plate 50 may be affixed to the lower section of the injector body 18 b by a retaining cap 74 .
- a fluid-retaining gasket 60 may be interposed between the whirl plate 50 and the lower portion of the injector body 18 b to prevent fluid from leaking between the mating surfaces of the whirl plate 50 , injector body 18 and retaining cap 74 .
- the gasket may comprise a silicone material.
- the upper injector body 18 a may include several sealing O-Rings 76 interposed between mating surfaces of the upper injector body 18 a and lower injector body 18 b, lower injector body 18 b and bottom plate 75 , bottom plate 75 and coil 38 , and coil 38 and upper injector body 18 a to prevent fluid leaks.
- FIGS. 4A and 4B show cross-section and exterior views, respectively, of an example embodiment of metering plug 26 .
- Metering plug 26 may have an end 28 formed to sealingly engage valve seat 24 , thereby closing exit orifice 22 from fluid communication with the whirl chamber 52 .
- Metering plug 26 may be movable within the whirl chamber 52 between the closed position shown in FIG. 2 and an open position wherein end 28 is removed from sealing engagement with valve seat 24 . In the open position, exit orifice 22 is opened to fluid communication with the whirl chamber 52 .
- Fluid may be delivered to the whirl chamber 52 via a fluid inlet 34 ( FIG. 2 ).
- Fluid inlet 34 may be in fluid communication with the whirl chamber 52 and may be externally connected to tank 10 via supply line 9 .
- Fluid such as aqueous urea reagent, may be pumped at a predetermined pressure setpoint into the fluid inlet 34 and into the whirl chamber 52 .
- the pressurized fluid may be accelerated to high velocity in the whirl slots 51 . This produces a high velocity rotating flow in the whirl chamber 52 .
- the predetermined pressure setpoint may vary in response to operating conditions to provide at least one of increased operating range and varied spray patterns from the exit orifice 22 .
- the predetermined pressure setpoint may be varied between approximately 50-200 psi, and for optimum results between approximately 60-150 psi.
- an actuator may be provided, for example in the form of magnetic coil 38 mounted in the injector body 18 .
- the magnet 38 When the magnet 38 is energized, the metering plug 26 is drawn upward from the closed position to the open position.
- the bottom plate 75 and the upper injector body 18 a may be constructed of magnetic stainless steel to provide a magnetized surface while retaining the corrosion resistant characteristics.
- the bottom injector body 18 b may be constructed of a non-magnetic stainless steel such as type 316 stainless steel. This enhances the isolation of the magnetic characteristic at the bottom plate 75 and limits the potential for the metering plug 26 to be magnetized toward the exit orifice 22 .
- the magnet would be energized, for example, in response to a signal from electronic controller 14 of FIG. 1 , which decides, based upon sensor input signals and its preprogrammed algorithms, when reagent is needed for effective selective catalytic reduction of NOx emissions in the exhaust stream.
- FIG. 5 shows an external view of the injector 16 connected to an exhaust tube 80 .
- Electrical connections 82 may be provided for providing a control signal to the injector 16 , for example from the reagent injection controller 14 ( FIG. 1 ).
- the magnetic coil 38 may be energized by a 12-24 VDC current with a pulse width modulated digital signal.
- the metering plug 26 includes a hollow section 90 which may be in fluid communication with the whirl chamber 52 via bores 92 in the metering plug 26 .
- the pressurized fluid from the whirl chamber 52 which is not expelled from exit orifice 22 may be forced into bores 92 , into the hollow section 90 and ultimately into outlet 36 through the hollow top portion 94 of the metering plug 26 .
- the fluid outlet 36 may be positioned as shown in FIG. 2 for removing fluid from the top portion 94 of the hollow section 90 of metering plug 26 .
- Fluid outlet 36 may be externally connected to return line 35 ( FIG. 5 ), thus permitting the fluid to circulate from the tank 10 of FIG.
- the fluid inlet 34 , fluid outlet 36 , and the hollow portion 90 of the metering plug 26 may provide a flow path for fluid flowing through the injector 16 , thereby enabling cooling of the injector 16 .
- the flow path for fluid through the injector 16 may be independent of the position of the metering plug 18 .
- a metering orifice 37 may be provided for controlling the amount of cooling fluid flowing through the injector 16 .
- the fluid inlet 34 may be proximate the whirl chamber 52 in a lower portion of the injector body 18 b and the fluid outlet 36 may be positioned in a top portion of the injector body, as shown in FIG. 1 .
- Cooling of the injector tip e.g., in the region of the valve seat 24 ) is of great importance to prevent solidification of the reagent in this area, which can result in clogging of the injector 16 .
- By positioning the fluid inlet 34 adjacent the whirl chamber in the lower portion of the injector body 18 b cooling at the injector tip is maximized since the fluid is not significantly heated by traveling through the injector body 16 .
- aqueous urea when used with this cooled injector 16 , will not solidify anywhere within the injector 16 , and in particular in the area of the whirl chamber 52 . If allowed to solidify, the urea could prevent metering plug 26 from seating properly or could cause the metering plug 26 to seize in either the open or closed position and/or the exit orifice 22 could become clogged. In addition, the detrimental effects of elevated temperature on the reagent, the moving parts, and the openings of the valve are avoided. In addition, by providing a cooling path through the entire length of the injector body, including directly cooling the injector tip in the region of the valve seat 24 , increased performance is achieved in comparison with the prior art, which provides only limited cooling of the injector.
- the increased cooling of the injector body in accordance with the present invention provides for prolonged life of the injector components, including the metering plug 26 and associated actuating components, and the valve seat 24 .
- Cooling ribs 72 provided on the exterior of the upper portion of the injector body 18 a provide additional cooling capacity.
- approximately 10 gallons of fluid may be circulated through the injector per hour. This flow rate may be varied depending on the application. For example, this flow rate may be varied from approximately 2 gallons per hour to approximately 20 gallons per hour.
- atomized fluid may be expelled at the rate of approximately 0.5-700 grams per minute, depending on the application and/or the control algorithm used, as well as the pressure setting and/or the size of the exit orifice 22 .
- the spray characteristics of fluid expelled from the exit orifice 22 may be varied depending on the pressure ratios of the pressure maintained in the return and supply lines. For example, the size of the droplets may be controlled by varying the pressure in the supply line 9 .
- the spray characteristics may be varied by interchanging different whirl plates.
- the whirl plate 50 which is affixed to the injector body by retaining cap 74 , may be removed and replaced with whirl plates with different sized exit orifices 22 , a different number of whirl slots 51 , or whirl slots of different length, depth or width.
- different whirl plates may be configured to provide larger or smaller whirl chambers 52 when affixed to lower section of the injector body 18 a.
- the fluid circulation rate can also be varied by modifying the internal diameter of metering orifice 37 . Varying the fluid circulation rate changes the droplet size and impacts the level of cooling provided by the fluid.
- Flow of the injector 16 can be varied for higher turndown (i.e., the ratio of maximum flow to minimum flow) from a given orifice diameter by changes in injector pulse-width modulation frequency, injector on-time and pressure setting.
- the pressure setting can be varied by any means including operation of a variable speed pump. This feature is particularly advantageous for exhaust gas treatment systems where a wide range of reagent flows may be needed based not only on engine operation but also on the condition of aftertreatment hardware such as traps or catalysts. Varying reagent pressure in the injector body between 80-120 psi has unexpectedly been found to provide turndown ratios in the range of approximately 5:1 and 50:1 when combined with changes in operating frequency and on-time of the injector 16 .
- Pressures of approximately 150-200 psi and as low as approximately 50-60 psi can also be used.
- a flow range of 12.6 gr/min to 517 gr/min was achieved by varying on-time from 1% to a maximum, with frequencies of 1.5 Hz to 10 Hz and operating pressure of 80 psi using a simulated hydrocarbon reagent marketed under the trade name of Viscor.
- Boosting the pump pressure to 120 psi increased the maximum flow rate to 631.0 gr/min at a frequency of 10 Hz and maximum injector on-time.
- a simple increase in voltage to the pump was used to adjust pump speed and consequently increase pressure of the reagent in the injector.
- the system was also operated at a steady pressure of 120 psi while varying frequency from 1.5 Hz to 10 Hz and injector on-time from 1% to a maximum, resulting in a flow range of 15.1 gr/min to 631 gr/min. Lower flows can be accomplished by selection of a smaller size for the exit orifice 22 .
- Use of the injector 16 of the present invention with an aqueous solution of 32.5% urea will generally provide flows at least 20% greater than that achieved with the simulated hydrocarbon reagent discussed above, due to density and viscosity differences between the urea reagent and the hydrocarbon reagent.
- a circular guide section 32 of the metering plug 26 may provide the main guiding function for sliding motion of the metering plug 26 within the chamber 30 .
- the tolerance between the circular guide section 32 and the chamber 30 is sufficient to allow relative motion and lubrication of the metering plug 26 while still guiding the metering plug's motion.
- the specific tolerances required at the various sections between the metering plug 26 and the chamber 30 will vary according to the operating temperature, operating pressure, the desired flow rate and circulation rate of the reagent, the tribological properties of the reagent and the materials chosen for the metering plug 26 and injector body 18 .
- the tolerances for optimum injector performance may be obtained experimentally through field trials.
- metering plug 26 may be biased in the closed position by a biasing member, which may be, for example, in the form of a coil spring 42 coaxially arranged with the hollow top portion 94 of the metering plug 26 , which serves as a spring seat against which the spring 42 can push to bias the metering plug 26 .
- a biasing member which may be, for example, in the form of a coil spring 42 coaxially arranged with the hollow top portion 94 of the metering plug 26 , which serves as a spring seat against which the spring 42 can push to bias the metering plug 26 .
- a thermal shield 58 may be mounted externally to the whirl plate 50 and retaining cap 74 prevents heat from the exhaust gases from being transferred to the whirl plate 50 and injector body 18 while simultaneously providing a heated surface ensuring that droplets unintentionally contacting the injector body do not form deposits.
- the thermal shield 58 may be made of inconel.
- the exit orifice 22 may be moved to the outside or injecting end of the whirl plate 50 , thereby increasing spray angle ⁇ and also allowing a wider range of spray angles while retaining the cooling properties.
- Thermal gasket 70 may be made of a flexible graphite foil sheathed in stainless steel material whose low thermal conductivity serves to isolate injector body 18 and the whirl plate 50 from the hot exhaust tube 80 , reducing conductive heat transfer to the injector 16 and thereby helping to keep the fluid circulating within the valve cool.
- the metering plug 26 may be made of type 430C or 440F stainless steel preferably coated with a coating that retains the urea corrosion resistance and the magnetic properties while reducing the metal fatigue caused over the life of the injector.
- the whirl plate 50 may be made of inconel or type 316 stainless steel and coated with a coating that retains the urea corrosion resistance while reducing the metal fatigue caused over the life of the injector 16 .
- the bottom plate 75 may be separated from the metering plug 26 and the metering plug 26 may be shortened to the shortest length reasonable for manufacturing to provide a significantly reduced metering plug mass.
- the decreased mass of the metering plug 26 prolongs the life of the plug, and in particular prolongs the life of the end 28 of the metering plug, which is subject to wear and deformation from repeated impact on the valve seat 24 .
- the present invention provides advantageous methods and apparatus for injecting an aqueous urea solution into the exhaust stream on an on-road diesel engine in order to reduce NOx emissions.
- the present invention is described above in connection with reducing NOx emissions in a diesel engine exhaust stream, the present invention is equally applicable to reducing NOx emissions in a natural gas or biodiesel engine exhaust stream.
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Abstract
Description
- This application is a continuation-in-part of co-pending, commonly assigned U.S. patent application Ser. No. 11/112,039 filed on Apr. 22, 2005, which claims the benefit of U.S. Provisional Application No. 60/565,356, filed Apr. 26, 2004.
- The present invention relates generally to the reduction of emissions produced by lean burn engines. In particular, the present invention provides methods and apparatus for injecting fluid, such as an aqueous urea solution, into an exhaust stream in order to reduce oxides of nitrogen (NOx) emissions from diesel engine exhaust.
- Lean burn engines provide improved fuel efficiency by operating with an excess of oxygen over the amount necessary for complete combustion of the fuel. Such engines are said to run “lean” or on a “lean mixture.” However, this increase in fuel economy is offset by undesired pollution emissions, specifically in the form of oxides of nitrogen (NOx).
- One method used to reduce NOx emissions from lean burn internal combustion engines is known as selective catalytic reduction (SCR). SCR, when used, for example, to reduce NOx emissions from a diesel engine, involves injecting an atomized reagent into the exhaust stream of the engine in relation to one or more selected engine operational parameters, such as exhaust gas temperature, engine rpm or engine load as measured by engine fuel flow, turbo boost pressure or exhaust NOx mass flow. The reagent/exhaust gas mixture is passed through a reactor containing a catalyst, such as, for example, activated carbon, or metals, such as platinum, vanadium or tungsten, which are capable of reducing the NOx concentration in the presence of the reagent. An SCR system of this type is disclosed in U.S. Pat. No. 5,976,475.
- An aqueous urea solution is known to be an effective reagent in SCR systems for diesel engines. However, use of such an aqueous urea solution involves many disadvantages. Urea is highly corrosive and attacks mechanical components of the SCR system, such as the injectors used to inject the urea mixture into the exhaust gas stream. Urea also tends to solidify upon prolonged exposure to high temperatures, such as encountered in diesel exhaust systems. Solidified urea will accumulate in the narrow passageways and exit orifice openings typically found in injectors. Solidified urea may foul moving parts of the injector and clog any openings, rendering the injector unusable.
- In addition, if the urea mixture is not finely atomized, urea deposits will form in the catalytic reactor, inhibiting the action of the catalyst and thereby reducing the SCR system effectiveness. High injection pressures are one way of minimizing the problem of insufficient atomization of the urea mixture. However, high injection pressures often result in over-penetration of the injector spray plume into the exhaust stream, causing the plume to impinge on the inner surface of the exhaust pipe opposite the injector. Over-penetration leads to inefficient use of the urea mixture and reduces the range over which the vehicle can operate with reduced NOx emissions. Only a finite amount of aqueous urea can be carried on a vehicle, and what is carried should be used efficiently to maximize vehicle range and reduce the need for frequent fill ups of the reagent.
- Further, aqueous urea is a poor lubricant. This characteristic adversely affects moving parts within the injector and requires that special fits, clearances and tolerances be employed between relatively moving parts within an injector. Aqueous urea also has a high propensity for leakage. This characteristic adversely affects mating surfaces requiring enhanced sealing resources in many locations.
- An example of a prior art injector for injecting aqueous urea into the exhaust stream of a lean bum diesel engine is described in U.S. Pat. No. 6,279,603. This prior art injector uses an atomizing hook external to the injector to cause dispersion of the urea solution expelled from the injector. The urea solution is circulated in the area of the exit orifice of the injector body to provide cooling.
- It would be advantageous to provide methods and apparatus for injecting an aqueous urea solution into the exhaust stream of a lean burn engine where atomizing of the urea solution occurs internally to the injector prior to being injected into the exhaust stream. It would be further advantageous to provide for cooling of the injector to prevent the urea from solidifying and to prolong the life of the injector components. It would be advantageous to minimize heat transfer to the injector from the exhaust pipe for minimal deposit formation internal to the injector. It would also be advantageous to minimize heat transfer from the hot gas to the exit orifice to prevent soot and urea from being attracted to the relatively cool injector exit orifice, creating deposits external to the injector. It would also be advantageous to provide an injector that does not leak for economical and environmental purposes.
- The methods and apparatus of the present invention provide the foregoing and other advantages.
- The present invention provides improved methods and apparatus for injecting fluid, such as an aqueous urea solution, into an exhaust stream in order to reduce oxides of nitrogen (NOx) emissions from diesel engine exhaust. In particular, the injector of the present invention is an enhanced performance atomizer for use with any diesel or natural gas engine.
- Current smaller displacement on and off-road diesel engine urea injectors utilize dual fluid atomization techniques. This process requires a separate air compressor. Other prior art atomization techniques, such as that disclosed in U.S. Pat. No. 6,279,603 ('603 patent) utilize an injector which does not have an atomization process internal to the injector. The injector described in the '603 patent sprays a free jet of liquid that produces small droplets upon impacting a hot plate or hook positioned on the outside of the injector body.
- The present invention provides improvements to prior art aqueous urea injectors, in particular, improvements to an aqueous urea injector of the type described in the '603 patent. The present invention utilizes atomization techniques that occur internal to the injector. In particular, the present invention uses mechanical spill return atomization techniques to produce droplets smaller than anticipated by the inventors, in particular, droplets approximately 50 μm SMD (Sauter mean diameter) or smaller. This size range is appropriate to allow urea to react into ammonia within the residence time associated with an on-road diesel engine, unlike the injector described in the '603 patent. This effect is achieved through the use of a whirl plate having a plurality of whirl slots surrounding the exit orifice of the injector, which produce a high velocity rotating flow in the whirl chamber. When a portion of the rotating flow of fluid is passed through the exit orifice into an exhaust stream, atomization occurs from a combination of centrifugal force and shearing of the fluid by air as it jets into the exhaust stream.
- In addition, the present invention provides further improvements over the injector of the '603 patent, including increased magnetic pull strength of the metering plug over a wide temperature range, prolonged life of the injector valve and associated actuating components, and cooling with the urea throughout the injector. Additionally, the present invention incorporates adjustable spray quality characteristics on line, and interchangeability of orifice plates for multiple size applications. The ribbed injector body provides additional cooling capability.
- The present invention may be further adapted to provide an injector for injecting hydrocarbons particularly for the purposes of regenerating a particulate filter in a diesel exhaust or for use in a hydrocarbon based lean-NOx catalyst system. The combination of pulse width modulation providing instantaneous timing control and mechanical atomization techniques is appropriate for providing small quantities of hydrocarbons with precise timing. The cooling aspects provided by the present invention allow the injector to survive the hot exhaust conditions as well as prevent pre-ignition of the hydrocarbon.
- In an example embodiment of the present invention, methods and apparatus for injecting atomized fluid are provided. An injector is provided, which comprises an injector body, and a whirl chamber arranged on the injector body. The whirl chamber has an exit orifice. A plurality of whirl slots may be provided in the whirl chamber for imparting a rotational velocity to fluid introduced into the whirl chamber. A valve seat positioned within the whirl chamber surrounds the exit orifice. A metering plug may be arranged within the injector body. An actuator may also be mounted on the injector body and connected to the metering plug for moving the metering plug between closed and open positions. The actuator may be located in the injector body and connected to the metering plug for enabling movement of the metering plug from the closed position to the open position.
- The metering plug may be located in the injector body such that when the metering plug is in a closed position, the metering plug is seated in the valve seat preventing fluid from being dispensed from the exit orifice. In one example embodiment, the fluid may be circulated through the injector to cool the injector when the metering plug is in the closed position. When the metering plug is in the open position, the metering plug is removed from the valve seat allowing fluid to be dispensed from the exit orifice. In the open position, the end of the metering plug is removed from the valve seat, and a portion of the rotating flow of fluid from the whirl chamber is passed through the exit orifice, where atomization occurs from a combination of centrifugal force and shearing of the fluid by air as it is dispensed into the exhaust stream.
- The injector may further comprise a fluid inlet extending into the injector and a fluid outlet extending out of the injector. The fluid inlet and fluid outlet may communicate with the whirl chamber via a hollow portion of the metering plug. The fluid inlet, the fluid outlet, and the hollow portion of the metering plug may provide a flow path for fluid through the injector, thereby enabling cooling of the injector. The flow path for the fluid through the injector may be provided independently of the position of the metering plug.
- A metering orifice located in the injector body may control the flow rate of cooling fluid flowing through the injector at a given inlet pressure. The fluid may be a urea solution or a hydrocarbon.
- In a further example embodiment, a plurality of ribs, surrounding the injector body, may be provided to disperse heat away from the injector body. A heat shield, surrounding the exit orifice, may also be provided to decrease the heat transfer from the exhaust stream to the injector body. The heat shield may have an aperture therethrough aligned with the exit orifice, thereby allowing fluid released from the whirl chamber to pass through the heat shield. The heat shield may comprise a plate surrounding the exit orifice and a layer of insulating material arranged on the plate.
- The injector body and metering plug may comprise stainless steel. A biasing member may be provided to bias the metering plug into the closed position, thereby providing a fail-closed valve. The biasing member may be a coil spring arranged coaxially with the metering plug.
- The actuator may comprise a magnetic coil generating a magnetic force. The magnetic force may effect a sliding motion of the metering plug against the biasing member when the magnetic coil is energized. The metering plug may thereby be moved from the closed position to the open position within the whirl chamber when the actuator is energized, enabling fluid to be dispensed from the exit orifice of the whirl chamber. Means for energizing the magnetic coil may be provided. For example, a 12 V pulse width modulated signal may energize the magnetic coil for a definite time period to inject a certain amount of fluid. Other means for energizing the magnetic coil which will be apparent to those skilled in the art may also be employed.
- A method of injecting a fluid into a gas stream is also provided in accordance with the invention. One example embodiment of such a method includes introducing a reagent into an injector body via a fluid inlet, providing a predetermined pressure setpoint for pressurizing the reagent in the injector body, imparting a high velocity rotating flow to at least a portion of the pressurized reagent within a whirl chamber of the injector body, and metering a precise amount of atomized reagent from an exit orifice into the exhaust gas stream. The predetermined pressure setpoint may be variable within a range of approximately 50 to 200 pounds per square inch. The whirl chamber may have a plurality of whirl slots. A fluid outlet may be provided for removing any reagent not metered into the exhaust stream from the injector body.
- The fluid in excess of the amount precisely metered may be circulated through the injector body to enable at least one of: (a) maintaining of the reagent within a desired temperature range; and (b) maintaining of the injector within a desired temperature range. A flow rate of the reagent circulating through the injector body may be variable from approximately 2 to 20 gallons per hour. The desired temperature range for the reagent may comprise 5° C. to 85° C.
- The reagent may comprise a urea solution, a hydrocarbon based reagent, or any other suitable reagent capable of reducing unwanted substances from engine exhaust streams. The exhaust gas stream may comprise a diesel engine exhaust stream or a natural gas or biodiesel engine exhaust stream.
- The predetermined pressure setpoint may be variable to provide at least one of increased operating range and varied spray patterns. Varying the predetermined pressure setpoint may vary an average droplet size of the atomized reagent metered into the exhaust gas stream. The average droplet size may be within a range of approximately 40 to 60 μm SMD.
- Varying the predetermined pressure setpoint may also vary a flow rate of the atomized reagent metered into the exhaust gas stream. The flow rate of the atomized reagent metered into the exhaust gas stream may be varied from approximately 0.5 to approximately 700 grams per minute (e.g., by varying at least one of the predetermined pressure, injector on-time, pulse width modulation frequency of the injector, and exit orifice size). Varying the flow rate further varies at least one of: (1) a droplet size of the atomized reagent metered into the exhaust gas stream; and (2) an amount of cooling provided by circulating reagent remaining in the injector body through the injector body.
- The plurality of whirl slots may comprise at least four whirl slots. The whirl slots may be arranged transversely to a longitudinal axis of the injector body. The whirl chamber may be provided in a whirl plate, which may be removable from the injector body. Thus, different whirl plates with correspondingly different characteristics can be interchanged in the injector body for different applications of the injector (e.g., different whirl plates to provide certain performance characteristics for passenger cars, light duty trucks, heavy duty trucks, generators, and the like). The different whirl plates may provide different spray patterns of the atomized reagent metered into the exhaust gas stream. Further, the different characteristics of the different whirl plates may comprise at least one of a different number of whirl slots, whirl slots of different length, whirl slots of different width, whirl slots of different depth, a differently sized whirl chamber, a differently sized exit orifice, and the like.
- In addition, a metering plug may be arranged within a lower section of the injector body. The metering of the reagent into the exhaust gas stream may be controlled via movement of the metering plug from between an open position opening the exit orifice and a closed position closing the exit orifice.
- A flow path may be provided for the reagent through the injector body. The flow path may comprise a fluid inlet arranged in the lower section of the injector body, a hollow portion extending through the metering plug, and a fluid outlet in an upper section of the injector body. The reagent may be continuously circulated through the flow path, thereby enabling continuous cooling of the injector in both the open and closed position of the metering plug.
- The fluid inlet may be proximate the whirl chamber in a lower portion of the injector body and the fluid outlet may be positioned in a top portion of the injector body. Cooling of the injector tip (e.g., in the region of the valve seat) is of great importance to prevent solidification of the reagent in this area, which can result in clogging of the injector. By positioning the fluid inlet adjacent the whirl chamber in the lower portion of the injector body, cooling at the injector tip is maximized since the fluid is not significantly heated by traveling through the injector body.
- Apparatus providing means to accomplish the methods described herein are also provided in accordance with the present invention.
- The present invention will hereinafter be described in conjunction with the appended drawing figures, wherein like numbers denote like elements, and:
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FIG. 1 shows a schematic diagram of an example embodiment of an on-road diesel engine with a pollution emission control system using an injector according to the present invention; -
FIG. 2 shows a longitudinal cross-sectional view of an example embodiment of an injector according to the invention; -
FIG. 3 (FIGS. 3A, 3B , and 3C) shows top, cross-sectional, and bottom views of an example embodiment of a whirl plate in accordance with the present invention; -
FIG. 4 (FIGS. 4A and 4B ) shows an example embodiment of a metering plug used in the injector ofFIG. 2 ; and -
FIG. 5 shows a perspective view of an example embodiment of an injector mounted on an exhaust tube in accordance with the present invention. - The ensuing detailed description provides exemplary embodiments only, and is not intended to limit the scope, applicability, or configuration of the invention. Rather, the ensuing detailed description of the exemplary embodiments will provide those skilled in the art with an enabling description for implementing an example embodiment of the invention. It should be understood that various changes may be made in the function and arrangement of elements without departing from the spirit and scope of the invention as set forth in the appended claims.
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FIG. 1 shows an example pollution control system for reducing NOx emissions from the exhaust of adiesel engine 21. InFIG. 1 , solid lines between the elements of the system denote fluid lines and dashed lines denote electrical connections. The system of the present invention may includereagent tank 10 for holding the reagent (e.g., aqueous urea) and adelivery module 12 for delivering the reagent from thetank 10. Thetank 10 anddelivery module 12 may form an integrated reagent tank/delivery module. Also provided as part of the system is an electronicinjection control unit 14, aninjector module 16, and anexhaust system 19 having at least onecatalyst bed 17. - The
delivery module 12 may comprise a pump that is supplied reagent from thetank 10 through an in-line filter 23 via asupply line 9. Thereagent tank 10 may be polypropylene, epoxy coated carbon steel, PVC, or stainless steel and sized according to the application (e.g., vehicle size, intended use of the vehicle, and the like). Thefilter 23 may include a housing constructed of rigid plastic or stainless steel with a removable cartridge. A pressure regulator (not shown) may be provided to maintain the system at predetermined pressure setpoint (e.g., approximately 50-200 psi) and may be located in thereturn line 35 from theinjector 16. A pressure sensor may be provided in the flexible line leading to thereagent injector 16. The system may also incorporate various freeze protection strategies to unthaw frozen urea or to prevent the urea from freezing. For example, during system operation, regardless of whether or not the injector is releasing reagent into the exhaust gases, reagent is circulated continuously between thetank 10 and theinjector 16 to cool the injector and minimize the dwell time of the reagent in the injector so that the reagent remains cool. Continuous reagent circulation is necessary for temperature-sensitive reagents, such as aqueous urea, which tend to solidify upon exposure to elevated temperatures of 300° C. to 650° C. as would be experienced in an engine exhaust system. It has been found to be important to keep the urea mixture below 140° C. and preferably in a lower operating range between 5° C. and 95° C. to provide a margin of safety ensuring that solidification of the urea is prevented. Solidified urea, if allowed to form, would foul the moving parts and openings of the injector, eventually rendering the injector useless. It will be recognized that flow rates will depend on engine size and NOx levels. - The amount of reagent required may vary with load, engine RPM, engine speed, exhaust gas temperature, exhaust gas flow, engine fuel injection timing, and desired NOx reduction. All or some of the engine operating parameters may be supplied from the
engine control unit 27 via the engine/vehicle databus to thereagent injection controller 14. The reagentinjection control unit 14 could also be included as part of theengine control unit 27 if the truck manufacturer agrees to provide that functionality. - Exhaust gas temperature, exhaust gas flow and exhaust back pressure may be measured by respective sensors.
- A minimum reagent level switch or programmed logic based on voltage may be used to prevent the injection system from running dry and overheating. Once a minimum reagent level in the
tank 10 is reached, injection will cease and a fault light and/or a text alarm will illuminate in the cab of the vehicle. - The injection rate may be set by programming the reagent
injection control unit 14 with an injection control strategy or map, as described in commonly owned co-pending U.S. Pat. No. 6,941,746 issued on Sep. 13, 2005 entitled “Mobile Diesel Selective Catalytic Reduction Systems and Methods” which is incorporated herein and made a part hereof by reference. As described therein, the injection strategy may be developed by temporarily installing aNOx detector 25 on the vehicle. TheNOx detector 25 may be a sensor or a meter with a sampling system.FIG. 1 shows aNOx meter 25 which analyzes the gas concentration or mass at a location external to theexhaust system 19. -
FIG. 2 shows a cross-sectional view of an example embodiment of theinjector 16 according to the present invention, which may be used in the system shown inFIG. 1 .Injector 16 may comprise aninjector body 18 having an upper section 18 a and alower section 18 b. An elongatedcylindrical chamber 30 may be disposed within theinjector body 18. Thechamber 30 may be in fluid communication with awhirl plate 50, which has anexit orifice 22 that opens onto the exhaust gases within the exhaust system 19 (FIG. 1 ) of a diesel engine when mounted thereon. Surroundingexit orifice 22 may be avalve seat 24 which can have any practical shape but is preferably conical. A valve member in the form of anelongated metering plug 26 may be slidably mounted within thechamber 30. -
FIG. 3A shows a top view of thewhirl plate 50.FIG. 3B shows a cross-sectional view of thewhirl plate 50.FIG. 3C shows a bottom view of thewhirl plate 50. As can be seen fromFIG. 3A , thewhirl plate 50 may include a plurality ofwhirl slots 51 surrounding thevalve seat 24 and forming awhirl chamber 52 in the area surrounding theend 28 of the metering plug 26 (seeFIG. 2 ). Thewhirl slots 51 may be arranged transversely to a longitudinal axis of theinjector body 18, as shown inFIG. 3A . As can be seen fromFIGS. 3A and 3B , thevalve seat 24 surrounds theexit orifice 22 for dispensing the atomized fluid from thewhirl chamber 52. Thewhirl plate 50 may be affixed to the lower section of theinjector body 18 b by a retainingcap 74. - In the example configuration shown, a fluid-retaining
gasket 60 may be interposed between thewhirl plate 50 and the lower portion of theinjector body 18 b to prevent fluid from leaking between the mating surfaces of thewhirl plate 50,injector body 18 and retainingcap 74. The gasket may comprise a silicone material. The upper injector body 18 a may include several sealing O-Rings 76 interposed between mating surfaces of the upper injector body 18 a andlower injector body 18 b,lower injector body 18 b andbottom plate 75,bottom plate 75 andcoil 38, andcoil 38 and upper injector body 18 a to prevent fluid leaks. -
FIGS. 4A and 4B show cross-section and exterior views, respectively, of an example embodiment ofmetering plug 26.Metering plug 26 may have anend 28 formed to sealingly engagevalve seat 24, thereby closingexit orifice 22 from fluid communication with thewhirl chamber 52.Metering plug 26 may be movable within thewhirl chamber 52 between the closed position shown inFIG. 2 and an open position whereinend 28 is removed from sealing engagement withvalve seat 24. In the open position,exit orifice 22 is opened to fluid communication with thewhirl chamber 52. - Fluid may be delivered to the
whirl chamber 52 via a fluid inlet 34 (FIG. 2 ).Fluid inlet 34 may be in fluid communication with thewhirl chamber 52 and may be externally connected totank 10 viasupply line 9. Fluid, such as aqueous urea reagent, may be pumped at a predetermined pressure setpoint into thefluid inlet 34 and into thewhirl chamber 52. The pressurized fluid may be accelerated to high velocity in thewhirl slots 51. This produces a high velocity rotating flow in thewhirl chamber 52. When theend 28 of the metering plug is removed from thevalve seat 24, a portion of the rotating flow of fluid is passed throughexit orifice 22, where atomization occurs from a combination of centrifugal force and shearing of the fluid by air as it jets into the exhaust stream. - The predetermined pressure setpoint may vary in response to operating conditions to provide at least one of increased operating range and varied spray patterns from the
exit orifice 22. For example, the predetermined pressure setpoint may be varied between approximately 50-200 psi, and for optimum results between approximately 60-150 psi. - To effect the opening and closing of the
exit orifice 22, an actuator may be provided, for example in the form ofmagnetic coil 38 mounted in theinjector body 18. When themagnet 38 is energized, themetering plug 26 is drawn upward from the closed position to the open position. Thebottom plate 75 and the upper injector body 18 a may be constructed of magnetic stainless steel to provide a magnetized surface while retaining the corrosion resistant characteristics. Thebottom injector body 18 b may be constructed of a non-magnetic stainless steel such as type 316 stainless steel. This enhances the isolation of the magnetic characteristic at thebottom plate 75 and limits the potential for themetering plug 26 to be magnetized toward theexit orifice 22. The magnet would be energized, for example, in response to a signal fromelectronic controller 14 ofFIG. 1 , which decides, based upon sensor input signals and its preprogrammed algorithms, when reagent is needed for effective selective catalytic reduction of NOx emissions in the exhaust stream. -
FIG. 5 shows an external view of theinjector 16 connected to anexhaust tube 80.Electrical connections 82 may be provided for providing a control signal to theinjector 16, for example from the reagent injection controller 14 (FIG. 1 ). Themagnetic coil 38 may be energized by a 12-24 VDC current with a pulse width modulated digital signal. - As shown in
FIG. 4A , themetering plug 26 includes ahollow section 90 which may be in fluid communication with thewhirl chamber 52 viabores 92 in themetering plug 26. The pressurized fluid from thewhirl chamber 52 which is not expelled fromexit orifice 22 may be forced intobores 92, into thehollow section 90 and ultimately intooutlet 36 through the hollowtop portion 94 of themetering plug 26. Thefluid outlet 36 may be positioned as shown inFIG. 2 for removing fluid from thetop portion 94 of thehollow section 90 ofmetering plug 26.Fluid outlet 36 may be externally connected to return line 35 (FIG. 5 ), thus permitting the fluid to circulate from thetank 10 ofFIG. 1 , throughsupply line 9, throughfluid inlet 34, into thewhirl chamber 52, throughbores 92, through thehollow section 90 ofmetering plug 26, out of hollowtop portion 94 and intofluid outlet 36, throughreturn line 35 and back intotank 10 ofFIG. 1 . This circulation keeps theinjector 16 cool and minimizes the dwell time of the fluid in the injector. Thefluid inlet 34,fluid outlet 36, and thehollow portion 90 of themetering plug 26 may provide a flow path for fluid flowing through theinjector 16, thereby enabling cooling of theinjector 16. The flow path for fluid through theinjector 16 may be independent of the position of themetering plug 18. Ametering orifice 37 may be provided for controlling the amount of cooling fluid flowing through theinjector 16. - The
fluid inlet 34 may be proximate thewhirl chamber 52 in a lower portion of theinjector body 18 b and thefluid outlet 36 may be positioned in a top portion of the injector body, as shown inFIG. 1 . Cooling of the injector tip (e.g., in the region of the valve seat 24) is of great importance to prevent solidification of the reagent in this area, which can result in clogging of theinjector 16. By positioning thefluid inlet 34 adjacent the whirl chamber in the lower portion of theinjector body 18 b, cooling at the injector tip is maximized since the fluid is not significantly heated by traveling through theinjector body 16. Thus, for example, aqueous urea, when used with this cooledinjector 16, will not solidify anywhere within theinjector 16, and in particular in the area of thewhirl chamber 52. If allowed to solidify, the urea could prevent metering plug 26 from seating properly or could cause themetering plug 26 to seize in either the open or closed position and/or theexit orifice 22 could become clogged. In addition, the detrimental effects of elevated temperature on the reagent, the moving parts, and the openings of the valve are avoided. In addition, by providing a cooling path through the entire length of the injector body, including directly cooling the injector tip in the region of thevalve seat 24, increased performance is achieved in comparison with the prior art, which provides only limited cooling of the injector. Further, the increased cooling of the injector body in accordance with the present invention provides for prolonged life of the injector components, including themetering plug 26 and associated actuating components, and thevalve seat 24. Coolingribs 72 provided on the exterior of the upper portion of the injector body 18 a provide additional cooling capacity. - As an example, approximately 10 gallons of fluid may be circulated through the injector per hour. This flow rate may be varied depending on the application. For example, this flow rate may be varied from approximately 2 gallons per hour to approximately 20 gallons per hour. Upon removing the
end 28 of themetering plug 26 from thevalve seat 24, atomized fluid may be expelled at the rate of approximately 0.5-700 grams per minute, depending on the application and/or the control algorithm used, as well as the pressure setting and/or the size of theexit orifice 22. The spray characteristics of fluid expelled from theexit orifice 22 may be varied depending on the pressure ratios of the pressure maintained in the return and supply lines. For example, the size of the droplets may be controlled by varying the pressure in thesupply line 9. In addition, the spray characteristics may be varied by interchanging different whirl plates. For example, thewhirl plate 50, which is affixed to the injector body by retainingcap 74, may be removed and replaced with whirl plates with differentsized exit orifices 22, a different number ofwhirl slots 51, or whirl slots of different length, depth or width. Further, different whirl plates may be configured to provide larger orsmaller whirl chambers 52 when affixed to lower section of the injector body 18 a. The fluid circulation rate can also be varied by modifying the internal diameter ofmetering orifice 37. Varying the fluid circulation rate changes the droplet size and impacts the level of cooling provided by the fluid. - Flow of the
injector 16 can be varied for higher turndown (i.e., the ratio of maximum flow to minimum flow) from a given orifice diameter by changes in injector pulse-width modulation frequency, injector on-time and pressure setting. The pressure setting can be varied by any means including operation of a variable speed pump. This feature is particularly advantageous for exhaust gas treatment systems where a wide range of reagent flows may be needed based not only on engine operation but also on the condition of aftertreatment hardware such as traps or catalysts. Varying reagent pressure in the injector body between 80-120 psi has unexpectedly been found to provide turndown ratios in the range of approximately 5:1 and 50:1 when combined with changes in operating frequency and on-time of theinjector 16. Pressures of approximately 150-200 psi and as low as approximately 50-60 psi can also be used. For example, in laboratory flow testing of one embodiment of theinjector 16 of the present invention having anexit orifice 22 with a 0.030″ diameter, a flow range of 12.6 gr/min to 517 gr/min was achieved by varying on-time from 1% to a maximum, with frequencies of 1.5 Hz to 10 Hz and operating pressure of 80 psi using a simulated hydrocarbon reagent marketed under the trade name of Viscor. Boosting the pump pressure to 120 psi increased the maximum flow rate to 631.0 gr/min at a frequency of 10 Hz and maximum injector on-time. A simple increase in voltage to the pump was used to adjust pump speed and consequently increase pressure of the reagent in the injector. The system was also operated at a steady pressure of 120 psi while varying frequency from 1.5 Hz to 10 Hz and injector on-time from 1% to a maximum, resulting in a flow range of 15.1 gr/min to 631 gr/min. Lower flows can be accomplished by selection of a smaller size for theexit orifice 22. Use of theinjector 16 of the present invention with an aqueous solution of 32.5% urea will generally provide flows at least 20% greater than that achieved with the simulated hydrocarbon reagent discussed above, due to density and viscosity differences between the urea reagent and the hydrocarbon reagent. - A
circular guide section 32 of themetering plug 26 may provide the main guiding function for sliding motion of themetering plug 26 within thechamber 30. The tolerance between thecircular guide section 32 and thechamber 30 is sufficient to allow relative motion and lubrication of themetering plug 26 while still guiding the metering plug's motion. - Generally the specific tolerances required at the various sections between the
metering plug 26 and thechamber 30 will vary according to the operating temperature, operating pressure, the desired flow rate and circulation rate of the reagent, the tribological properties of the reagent and the materials chosen for themetering plug 26 andinjector body 18. The tolerances for optimum injector performance may be obtained experimentally through field trials. - As seen in
FIG. 2 ,metering plug 26 may be biased in the closed position by a biasing member, which may be, for example, in the form of acoil spring 42 coaxially arranged with the hollowtop portion 94 of themetering plug 26, which serves as a spring seat against which thespring 42 can push to bias themetering plug 26. - In the configuration shown, a
thermal shield 58 may be mounted externally to thewhirl plate 50 and retainingcap 74 prevents heat from the exhaust gases from being transferred to thewhirl plate 50 andinjector body 18 while simultaneously providing a heated surface ensuring that droplets unintentionally contacting the injector body do not form deposits. For example, thethermal shield 58 may be made of inconel. Alternatively, theexit orifice 22 may be moved to the outside or injecting end of thewhirl plate 50, thereby increasing spray angle α and also allowing a wider range of spray angles while retaining the cooling properties.Thermal gasket 70 may be made of a flexible graphite foil sheathed in stainless steel material whose low thermal conductivity serves to isolateinjector body 18 and thewhirl plate 50 from thehot exhaust tube 80, reducing conductive heat transfer to theinjector 16 and thereby helping to keep the fluid circulating within the valve cool. - The
metering plug 26 may be made of type 430C or 440F stainless steel preferably coated with a coating that retains the urea corrosion resistance and the magnetic properties while reducing the metal fatigue caused over the life of the injector. Thewhirl plate 50 may be made of inconel or type 316 stainless steel and coated with a coating that retains the urea corrosion resistance while reducing the metal fatigue caused over the life of theinjector 16. Thebottom plate 75 may be separated from themetering plug 26 and themetering plug 26 may be shortened to the shortest length reasonable for manufacturing to provide a significantly reduced metering plug mass. The decreased mass of themetering plug 26 prolongs the life of the plug, and in particular prolongs the life of theend 28 of the metering plug, which is subject to wear and deformation from repeated impact on thevalve seat 24. - It should now be appreciated that the present invention provides advantageous methods and apparatus for injecting an aqueous urea solution into the exhaust stream on an on-road diesel engine in order to reduce NOx emissions. Although the present invention is described above in connection with reducing NOx emissions in a diesel engine exhaust stream, the present invention is equally applicable to reducing NOx emissions in a natural gas or biodiesel engine exhaust stream.
- Although the invention has been described in connection with various illustrated embodiments, numerous modifications and adaptations may be made thereto without departing from the spirit and scope of the invention as set forth in the claims.
Claims (24)
Priority Applications (2)
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US12/275,539 US8047452B2 (en) | 2004-04-26 | 2008-11-21 | Method and apparatus for injecting atomized fluids |
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Cited By (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20090094968A1 (en) * | 2007-10-12 | 2009-04-16 | Mazda Motor Corporation | Exhaust-gas purification device disposition structure of vehicle |
US20090137350A1 (en) * | 2007-11-26 | 2009-05-28 | Jason Lenig | Game Ball with Enhanced in Flight Movement |
US20090297417A1 (en) * | 2008-05-27 | 2009-12-03 | Fuel Tech, Inc. | SELECTIVE CATALYTIC NOx REDUCTION PROCESS AND APPARATUS PROVIDING IMPROVED GASSIFICATION OF UREA TO FORM AMMONIA-CONTAINING GAS |
US20100122521A1 (en) * | 2008-11-19 | 2010-05-20 | Caterpillar Inc. | Method for purging a dosing system |
US20100300074A1 (en) * | 2009-05-28 | 2010-12-02 | Gm Global Technology Operations, Inc. | Exhaust hydrocarbon injection control system and method |
US20100313553A1 (en) * | 2009-06-11 | 2010-12-16 | Stanadyne Corporation | Integrated pump and injector for exhaust after treatment |
US20100314470A1 (en) * | 2009-06-11 | 2010-12-16 | Stanadyne Corporation | Injector having swirl structure downstream of valve seat |
US20110253807A1 (en) * | 2010-04-16 | 2011-10-20 | Daniel William Bamber | Pressure swirl atomizer with closure assist |
US20120003110A1 (en) * | 2010-07-02 | 2012-01-05 | Delphi Technologies Holding S.Arl | Pump for dosing fluids |
US20120006011A1 (en) * | 2007-02-28 | 2012-01-12 | Scion-Sprays Limited | Injection system for an internal combustion engine |
US8549840B2 (en) | 2010-11-12 | 2013-10-08 | Cummins Cal Pacific, Llc | Fluid injector |
DE102014111444A1 (en) | 2013-10-02 | 2015-04-02 | Denso Corporation | emission Control system |
US20190091604A1 (en) * | 2017-09-22 | 2019-03-28 | Tenneco Automotive Operating Company Inc. | Method And Apparatus For Preparation Of A Urea Solution |
US20190091615A1 (en) * | 2017-09-22 | 2019-03-28 | Tenneco Automotive Operating Company Inc. | Method And Apparatus For Preparation Of A Urea Solution |
US10900401B2 (en) * | 2016-08-17 | 2021-01-26 | Robert Bosch Gmbh | Method for detecting a blocked pressure line |
Families Citing this family (79)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7467749B2 (en) * | 2004-04-26 | 2008-12-23 | Tenneco Automotive Operating Company Inc. | Methods and apparatus for injecting atomized reagent |
US8047452B2 (en) * | 2004-04-26 | 2011-11-01 | Tenneco Automotive Operating Company Inc. | Method and apparatus for injecting atomized fluids |
PL1676988T3 (en) * | 2004-12-30 | 2008-03-31 | Grundfos No Nox As | Dosing pump unit |
ATE444801T1 (en) * | 2004-12-30 | 2009-10-15 | Grundfos Nonox As | DOSING PUMP UNIT |
DE502004005576D1 (en) * | 2004-12-30 | 2008-01-03 | Grundfos Nonox As | Device for generating a reducing agent-air mixture |
US20070158466A1 (en) * | 2005-12-29 | 2007-07-12 | Harmon Michael P | Nozzle assembly |
US20070228191A1 (en) * | 2006-03-31 | 2007-10-04 | Caterpillar Inc. | Cooled nozzle assembly for urea/water injection |
US20070235556A1 (en) * | 2006-03-31 | 2007-10-11 | Harmon Michael P | Nozzle assembly |
GB0607851D0 (en) * | 2006-04-24 | 2006-05-31 | Johnson Matthey Plc | Particulate matter generator |
DE102006022582A1 (en) * | 2006-05-15 | 2007-11-22 | Siemens Ag | Leak-free injection valve, injection device and method and apparatus for operating an internal combustion engine |
KR101460967B1 (en) * | 2006-05-31 | 2014-11-13 | 테네코 오토모티브 오퍼레이팅 컴파니 인코포레이티드 | Method and apparatus for reducing emissions in diesel engines |
US20090205316A1 (en) * | 2006-07-13 | 2009-08-20 | Inergy Automotive Systems Research (Societe Anonyme) | System and processes for storing an additive and injecting it into the exhaust gases of an engine |
US7497077B2 (en) * | 2006-07-26 | 2009-03-03 | Southwest Research Institute | System and method for dispensing an aqueous urea solution into an exhaust gas stream |
DE102006041663A1 (en) * | 2006-09-06 | 2008-03-27 | Daimler Ag | Exhaust system of a motor vehicle |
DE102006044080B4 (en) | 2006-09-20 | 2023-10-12 | Robert Bosch Gmbh | Method for operating a reagent metering valve and device for carrying out the method |
US8109077B2 (en) * | 2006-10-11 | 2012-02-07 | Tenneco Automotive Operating Company Inc. | Dual injector system for diesel emissions control |
DE102006053556A1 (en) * | 2006-11-14 | 2008-05-15 | Purem Abgassysteme Gmbh & Co. Kg | Device for dosing reducing agent and injector in a device for dosing reducing agent |
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US8171721B2 (en) | 2007-01-22 | 2012-05-08 | International Engine Intellectual Property Company, Llc | Closed loop control of exhaust system fluid dosing |
US7930878B2 (en) * | 2007-02-27 | 2011-04-26 | Ford Global Technologies, Llc | Method and apparatus for rapidly thawing frozen NOx reductant |
EP2538049B1 (en) * | 2007-03-30 | 2015-03-18 | Continental Automotive Systems US, Inc. | Reductant delivery unit for selective catalytic reduction |
FR2916250B1 (en) * | 2007-05-14 | 2010-08-27 | Renault Sas | CONNECTING A TURBOCHARGER WITH AN OXIDATION CATALYST OF AN EXHAUST LINE OF AN INTERNAL COMBUSTION ENGINE |
DE102007024782B4 (en) * | 2007-05-26 | 2011-08-25 | Eichenauer Heizelemente GmbH & Co. KG, 76870 | Heating insert and its use in a urea supply system |
FR2921107A1 (en) * | 2007-09-14 | 2009-03-20 | Inergy Automotive Systems Res | METHOD AND SYSTEM FOR INJECTING A LIQUID |
DE102008050357A1 (en) * | 2007-10-09 | 2009-04-30 | Mitsubishi Fuso Truck and Bus Corp., Kawasaki | Exhaust gas purification device for a motor |
JP2009097438A (en) * | 2007-10-17 | 2009-05-07 | Mitsubishi Fuso Truck & Bus Corp | Exhaust emission control system |
US20090114864A1 (en) * | 2007-11-05 | 2009-05-07 | Eaton Corporation | Failsafe fuel doser solenoid valve using a reversible electrical coil assembly |
DE102008002286A1 (en) * | 2008-06-09 | 2009-12-10 | Robert Bosch Gmbh | Exhaust after-treatment device for an internal combustion engine with an SCR catalytic converter and method for operating an internal combustion engine |
US8038952B2 (en) * | 2008-08-28 | 2011-10-18 | General Electric Company | Surface treatments and coatings for flash atomization |
US7980483B2 (en) * | 2008-10-13 | 2011-07-19 | Eaton Corporation | Injector for a fluid injection system |
DK2189633T3 (en) * | 2008-11-22 | 2012-02-20 | Grundfos Management As | Device for discharging urea solution to an exhaust gas line |
JP4911193B2 (en) * | 2009-04-28 | 2012-04-04 | 株式会社デンソー | Exhaust gas purification system for internal combustion engine |
DE102009025226A1 (en) * | 2009-06-09 | 2010-12-16 | Elringklinger Ag | System for injecting urea solution on exhaust line of internal combustion engine, has reservoir for urea, and has nozzle that is injected in exhaust line |
US8468810B2 (en) * | 2009-12-04 | 2013-06-25 | Tenneco Automotive Operating Company Inc. | NOx elimination injector firing control circuit |
US8429903B2 (en) * | 2009-12-22 | 2013-04-30 | Caterpillar Inc. | Radial mounting for regeneration device |
FR2955188B1 (en) * | 2010-01-12 | 2013-05-31 | Peugeot Citroen Automobiles Sa | METHOD OF CALCULATING A SET-UP OF A REDUCING FLUID IN AN EXHAUST LINE |
US8973895B2 (en) | 2010-02-10 | 2015-03-10 | Tenneco Automotive Operating Company Inc. | Electromagnetically controlled injector having flux bridge and flux break |
WO2011100337A2 (en) * | 2010-02-10 | 2011-08-18 | Tenneco Automotive Operating Company Inc. | Pressure swirl flow injector with reduced flow variability and return flow |
US8740113B2 (en) | 2010-02-10 | 2014-06-03 | Tenneco Automotive Operating Company, Inc. | Pressure swirl flow injector with reduced flow variability and return flow |
US9683472B2 (en) | 2010-02-10 | 2017-06-20 | Tenneco Automotive Operating Company Inc. | Electromagnetically controlled injector having flux bridge and flux break |
CN101988412A (en) * | 2010-11-12 | 2011-03-23 | 无锡市凯龙汽车设备制造有限公司 | SCR (selective catalyst reduction) injector head of diesel engine |
DE102011010641A1 (en) * | 2011-02-09 | 2012-08-09 | Emitec France S.A.S | Injector for a urea-water solution |
WO2012138373A1 (en) * | 2011-04-04 | 2012-10-11 | Mack Trucks, Inc. | Fluid cooled injector and exhaust aftertreatment system, vehicle, and method using a fluid cooled injector |
US8635854B2 (en) * | 2011-08-05 | 2014-01-28 | Tenneco Automotive Operating Company Inc. | Reductant injection control system |
SE537849C2 (en) * | 2011-09-22 | 2015-11-03 | Scania Cv Ab | Method and system for determining need for review of a dosage unit in an SCR system |
US8701389B2 (en) | 2011-12-06 | 2014-04-22 | Tenneco Automotive Operating Company Inc. | Reagent injector control system |
BR112014014298A2 (en) * | 2011-12-14 | 2017-06-13 | Scania Cv Ab | method belonging to a scr system and a scr system |
US8591849B2 (en) | 2012-04-16 | 2013-11-26 | Combustion Components Associates, Inc. | On demand generation of ammonia for small industrial and commercial boilers |
DE102012206481A1 (en) * | 2012-04-19 | 2013-10-24 | Robert Bosch Gmbh | metering |
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DE102012010980A1 (en) * | 2012-06-02 | 2013-12-05 | Hydac Electronic Gmbh | System for exhaust aftertreatment in internal combustion engines |
US8815197B2 (en) | 2012-10-05 | 2014-08-26 | Peerless Mfg. Co. | Method for urea decomposition and ammonia feed to a selective catalytic reduction system |
US8815196B2 (en) | 2012-10-05 | 2014-08-26 | Peerless Mfg. Co. | Method for in-duct urea injection for selective catalytic reduction on small boilers and combustion sources |
DE102012219828A1 (en) * | 2012-10-30 | 2014-04-30 | Robert Bosch Gmbh | Injection valve and exhaust aftertreatment device |
US9746177B2 (en) | 2012-11-12 | 2017-08-29 | Peerless Mfg. Co. | Urea decomposition and improved SCR NOx reduction on industrial and small utility boilers |
US8806853B2 (en) | 2012-12-05 | 2014-08-19 | Cummins Powergen Ip, Inc. | System and method for SCR inducement |
US9771847B2 (en) | 2012-12-05 | 2017-09-26 | Cummins Cal Pacific, Llc | Integrated load bank and exhaust heater system with load shed capability for a diesel genset exhaust aftertreatment system |
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US9333466B2 (en) | 2012-12-05 | 2016-05-10 | Cummins Powergen Ip, Inc. | Diesel exhaust fluid injector assembly |
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US9664082B2 (en) | 2014-06-02 | 2017-05-30 | Caterpillar Inc. | Reductant dosing system having staggered injectors |
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Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5570841A (en) * | 1994-10-07 | 1996-11-05 | Siemens Automotive Corporation | Multiple disk swirl atomizer for fuel injector |
US6279603B1 (en) * | 1998-10-01 | 2001-08-28 | Ambac International | Fluid-cooled injector |
US20020092930A1 (en) * | 2001-01-17 | 2002-07-18 | Ryuji Itatsu | Nozzles suitable for use with fluid injectors |
US20020194841A1 (en) * | 2000-10-16 | 2002-12-26 | Engelhard Corporation | Method for determining catalyst cool down temperature |
US7467749B2 (en) * | 2004-04-26 | 2008-12-23 | Tenneco Automotive Operating Company Inc. | Methods and apparatus for injecting atomized reagent |
Family Cites Families (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2235834A (en) * | 1939-06-01 | 1941-03-25 | Claude S Gillette | Fuel oil burner nozzle |
DE2460111A1 (en) | 1974-04-13 | 1976-07-15 | Daimler Benz Ag | INJECTION VALVE |
DE2418227C3 (en) | 1974-04-13 | 1978-09-14 | Daimler-Benz Ag, 7000 Stuttgart | Low-pressure injection valve for introducing liquid fuel into the combustion chamber of an internal combustion engine |
JPS6042351B2 (en) | 1978-11-07 | 1985-09-21 | 株式会社豊田中央研究所 | Reflux type volute injection valve |
US4742964A (en) * | 1985-10-30 | 1988-05-10 | Aisan Kogyo Kabushiki Kaisha | Electromagnetic fuel injector |
JPH02503101A (en) * | 1986-10-30 | 1990-09-27 | ジーメンス・アクティエンゲゼルシャフト | high pressure swirl injector |
US4805837A (en) | 1986-10-30 | 1989-02-21 | Allied Corporation | Injector with swirl chamber return |
US5307997A (en) * | 1993-03-12 | 1994-05-03 | Siemens Automotive L.P. | Fuel injector swirl passages |
US5522218A (en) | 1994-08-23 | 1996-06-04 | Caterpillar Inc. | Combustion exhaust purification system and method |
DE4436397B4 (en) * | 1994-10-12 | 2006-06-08 | Robert Bosch Gmbh | Device for aftertreatment of exhaust gases |
US5713327A (en) | 1997-01-03 | 1998-02-03 | Tilton; Charles L. | Liquid fuel injection device with pressure-swirl atomizers |
US5976475A (en) | 1997-04-02 | 1999-11-02 | Clean Diesel Technologies, Inc. | Reducing NOx emissions from an engine by temperature-controlled urea injection for selective catalytic reduction |
US6063350A (en) | 1997-04-02 | 2000-05-16 | Clean Diesel Technologies, Inc. | Reducing nox emissions from an engine by temperature-controlled urea injection for selective catalytic reduction |
US5924280A (en) | 1997-04-04 | 1999-07-20 | Clean Diesel Technologies, Inc. | Reducing NOx emissions from an engine while maximizing fuel economy |
US5884611A (en) * | 1997-10-14 | 1999-03-23 | Cummins Engine Company, Inc. | Effervescent injector for diesel engines |
DE19806265C5 (en) | 1998-02-16 | 2004-07-22 | Siemens Ag | dosing |
DE19901915C1 (en) | 1999-01-19 | 2000-04-20 | Siemens Ag | Catalytic conversion of nitrogen oxides in exhaust gases using urea reductant is controlled by time differentiation of engine operational parameter, adjusting reductant excess more swiftly as a function of the result |
US6257496B1 (en) * | 1999-12-23 | 2001-07-10 | Siemens Automotive Corporation | Fuel injector having an integrated seat and swirl generator |
DE10116214A1 (en) * | 2001-03-30 | 2002-10-10 | Bosch Gmbh Robert | Device for the aftertreatment of exhaust gases from an internal combustion engine |
JP3888519B2 (en) * | 2001-09-12 | 2007-03-07 | 株式会社デンソー | Exhaust purification device |
US6922987B2 (en) * | 2003-02-12 | 2005-08-02 | Fleetguard, Inc. | System and method for enhancing internal combustion engine aftertreatment applications by superheated fuel injection |
US7021558B2 (en) * | 2003-04-25 | 2006-04-04 | Cummins Inc. | Fuel injector having a cooled lower nozzle body |
-
2005
- 2005-04-22 US US11/112,039 patent/US7467749B2/en active Active
- 2005-04-25 EP EP05741327A patent/EP1751407B1/en active Active
- 2005-04-25 CA CA2563764A patent/CA2563764C/en not_active Expired - Fee Related
- 2005-04-25 AT AT05741327T patent/ATE540205T1/en active
- 2005-04-25 WO PCT/US2005/014289 patent/WO2005104723A2/en active Application Filing
-
2007
- 2007-02-15 US US11/707,463 patent/US20070138322A1/en not_active Abandoned
- 2007-03-05 US US11/714,718 patent/US20080087739A1/en not_active Abandoned
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5570841A (en) * | 1994-10-07 | 1996-11-05 | Siemens Automotive Corporation | Multiple disk swirl atomizer for fuel injector |
US6279603B1 (en) * | 1998-10-01 | 2001-08-28 | Ambac International | Fluid-cooled injector |
US20020194841A1 (en) * | 2000-10-16 | 2002-12-26 | Engelhard Corporation | Method for determining catalyst cool down temperature |
US20020092930A1 (en) * | 2001-01-17 | 2002-07-18 | Ryuji Itatsu | Nozzles suitable for use with fluid injectors |
US7467749B2 (en) * | 2004-04-26 | 2008-12-23 | Tenneco Automotive Operating Company Inc. | Methods and apparatus for injecting atomized reagent |
Cited By (27)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20120006011A1 (en) * | 2007-02-28 | 2012-01-12 | Scion-Sprays Limited | Injection system for an internal combustion engine |
US20090094968A1 (en) * | 2007-10-12 | 2009-04-16 | Mazda Motor Corporation | Exhaust-gas purification device disposition structure of vehicle |
US8056671B2 (en) * | 2007-10-12 | 2011-11-15 | Mazda Motor Corporation | Exhaust-gas purification device disposition structure of vehicle |
US20090137350A1 (en) * | 2007-11-26 | 2009-05-28 | Jason Lenig | Game Ball with Enhanced in Flight Movement |
US8852542B2 (en) * | 2008-05-27 | 2014-10-07 | Fuel Tech, Inc. | Selective catalytic NOx reduction process and apparatus providing improved gassification of urea to form ammonia-containing gas |
US20090297417A1 (en) * | 2008-05-27 | 2009-12-03 | Fuel Tech, Inc. | SELECTIVE CATALYTIC NOx REDUCTION PROCESS AND APPARATUS PROVIDING IMPROVED GASSIFICATION OF UREA TO FORM AMMONIA-CONTAINING GAS |
AU2009260566B2 (en) * | 2008-05-27 | 2013-08-22 | Fuel Tech, Inc. | Selective catalytic NOx reduction process and apparatus providing improved gasification of urea to form ammonia-containing gas |
US20100122521A1 (en) * | 2008-11-19 | 2010-05-20 | Caterpillar Inc. | Method for purging a dosing system |
US8459012B2 (en) | 2008-11-19 | 2013-06-11 | Caterpillar Inc. | Method for purging a dosing system |
US20100300074A1 (en) * | 2009-05-28 | 2010-12-02 | Gm Global Technology Operations, Inc. | Exhaust hydrocarbon injection control system and method |
US8156736B2 (en) * | 2009-05-28 | 2012-04-17 | GM Global Technology Operations LLC | Exhaust hydrocarbon injection control system and method |
US20100314470A1 (en) * | 2009-06-11 | 2010-12-16 | Stanadyne Corporation | Injector having swirl structure downstream of valve seat |
US20100313553A1 (en) * | 2009-06-11 | 2010-12-16 | Stanadyne Corporation | Integrated pump and injector for exhaust after treatment |
US8225602B2 (en) * | 2009-06-11 | 2012-07-24 | Stanadyne Corporation | Integrated pump and injector for exhaust after treatment |
WO2011130610A3 (en) * | 2010-04-16 | 2012-01-12 | Eaton Corporation | Pressure swirl atomizer with closure assist |
WO2011130610A2 (en) * | 2010-04-16 | 2011-10-20 | Eaton Corporation | Pressure swirl atomizer with closure assist |
US8523089B2 (en) * | 2010-04-16 | 2013-09-03 | International Engine Intellectual Property Company, Llc | Pressure swirl atomizer with closure assist |
US20110253807A1 (en) * | 2010-04-16 | 2011-10-20 | Daniel William Bamber | Pressure swirl atomizer with closure assist |
US20120003110A1 (en) * | 2010-07-02 | 2012-01-05 | Delphi Technologies Holding S.Arl | Pump for dosing fluids |
US9617987B2 (en) * | 2010-07-02 | 2017-04-11 | Delphi International Operations Luxembourg S.A.R.L. | Pump for dosing fluids |
US8549840B2 (en) | 2010-11-12 | 2013-10-08 | Cummins Cal Pacific, Llc | Fluid injector |
DE102014111444A1 (en) | 2013-10-02 | 2015-04-02 | Denso Corporation | emission Control system |
US9222391B2 (en) | 2013-10-02 | 2015-12-29 | Denso Corporation | Exhaust gas purification system |
DE102014111444B4 (en) | 2013-10-02 | 2024-01-04 | Denso Corporation | Exhaust gas purification system with cooling section for an additional valve |
US10900401B2 (en) * | 2016-08-17 | 2021-01-26 | Robert Bosch Gmbh | Method for detecting a blocked pressure line |
US20190091604A1 (en) * | 2017-09-22 | 2019-03-28 | Tenneco Automotive Operating Company Inc. | Method And Apparatus For Preparation Of A Urea Solution |
US20190091615A1 (en) * | 2017-09-22 | 2019-03-28 | Tenneco Automotive Operating Company Inc. | Method And Apparatus For Preparation Of A Urea Solution |
Also Published As
Publication number | Publication date |
---|---|
CA2563764A1 (en) | 2005-11-10 |
EP1751407A4 (en) | 2009-04-01 |
ATE540205T1 (en) | 2012-01-15 |
US20050235632A1 (en) | 2005-10-27 |
US7467749B2 (en) | 2008-12-23 |
CA2563764C (en) | 2013-07-09 |
EP1751407B1 (en) | 2012-01-04 |
US20070138322A1 (en) | 2007-06-21 |
WO2005104723A3 (en) | 2007-04-05 |
EP1751407A2 (en) | 2007-02-14 |
WO2005104723A2 (en) | 2005-11-10 |
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