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:
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.
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. For example, during system operation, regardless of whether or not the injector is releasing reagent into the exhaust gases, 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. 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 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. As described therein, 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.
In the example configuration shown, a fluid-retaining gasket 60 may be interposed between the whirl plate 50 and the lower portion of the injector body 18b 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 18a may include several sealing O-Rings 76 interposed between mating surfaces of the upper injector body 18a and lower injector body 18b, lower injector body 18b and bottom plate 75, bottom plate 75 and coil 38, and coil 38 and upper injector body 18a to prevent fluid leaks.
Fluid may be delivered to the whirl chamber 52 via a fluid inlet 34 (
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 of magnetic coil 38 mounted in the injector body 18. 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 18a may be constructed of magnetic stainless steel to provide a magnetized surface while retaining the corrosion resistant characteristics. The bottom injector body 18b 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
As shown in
The fluid inlet 34 may be proximate the whirl chamber 52 in a lower portion of the injector body 18b and the fluid outlet 36 may be positioned in a top portion of the injector body, as shown in
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 the metering plug 26 from the valve 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 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. In addition, the spray characteristics may be varied by interchanging different whirl plates. For example, 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. Further, different whirl plates may be configured to provide larger or smaller whirl chambers 52 when affixed to lower section of the injector body 18a. 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. For example, in laboratory flow testing of one embodiment of the injector 16 of the present invention having an exit 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 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.
Generally 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.
As seen in
In the configuration shown, 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. For example, the thermal shield 58 may be made of inconel. Alternatively, the exit orifice 22 may be moved to the outside or injecting end of the whirl 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 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.
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.
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.
Number | Date | Country | |
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60565356 | Apr 2004 | US |
Number | Date | Country | |
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Parent | 11112039 | Apr 2005 | US |
Child | 11714718 | Mar 2007 | US |