US20140054396A1 - Fluid injector - Google Patents
Fluid injector Download PDFInfo
- Publication number
- US20140054396A1 US20140054396A1 US13/621,838 US201213621838A US2014054396A1 US 20140054396 A1 US20140054396 A1 US 20140054396A1 US 201213621838 A US201213621838 A US 201213621838A US 2014054396 A1 US2014054396 A1 US 2014054396A1
- Authority
- US
- United States
- Prior art keywords
- injector
- fluid
- passage
- valve
- flow
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Images
Classifications
-
- 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
- F01N3/24—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 constructional aspects of converting apparatus
-
- 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
- F01N3/24—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 constructional aspects of converting apparatus
- F01N3/36—Arrangements for supply of additional fuel
-
- 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
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
-
- 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
- F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
-
- 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
- DPFs diesel particulate filters
- a DPF has a structure that permits exhaust gases to flow through the filter while trapping solid particulate matter. Over time, the accumulated particulate matter can reduce the efficiency of the filter. Accordingly, various methods are used to clean or “regenerate” the filter to its original state by burning off the trapped particulate matter.
- active regeneration One method for cleaning the DPF is referred to as “active regeneration.”
- active regeneration the exhaust gas temperature is increased to levels to “burn off” the accumulated particulate matter in the DPF.
- an injector commonly referred to as “closer” can be used to periodically inject diesel fuel (or other reagent) into the engine exhaust upstream of the DPF.
- the injected fuel is burned to raise the temperature of the exhaust gas entering the DPF to a level sufficient to burn off the accumulated soot.
- the elevated temperature of the exhaust gas entering the DPF may be generated in a diesel oxidation catalyst (DOC) located upstream of the DPF.
- DOC diesel oxidation catalyst
- the doser injects fuel exhaust stream upstream of the DOC.
- the DOC consumes the fuel, resulting in an exothermic reaction in the DOC, which elevates the temperature of the exhaust gas flowing downstream to the DPF to approximately and/or above 550° C., causing the “burn off” event and DPF regeneration.
- SCR selective catalytic reduction
- a catalyst which reduces NO x concentration in the presence of the reagent.
- Injectors that are used for DPF regeneration and SCR typically inject the reagent directly into the engine exhaust flow. As such, these injectors can be exposed to harsh operating conditions, including elevated temperatures and contaminants within the exhaust stream. In such an environment, soot can accumulate in and around the tip of the injector. With time, the soot build up can lead to a reduced flow through the injector, poor atomization, or even a complete loss of flow if the injector becomes completely covered, or plugged. This phenomena is commonly referred to in the art as “injector fouling.”
- Embodiments depicted herein disclose an injector for injecting fluid, such as diesel fuel, ammonia, urea or other reagent, into an engine exhaust stream while reducing the occurrence of injector fouling.
- fluid such as diesel fuel, ammonia, urea or other reagent
- the presently described technology involves an injector for controllably injecting a fluid into an exhaust stream having a housing that defines a chamber for storing the fluid and an orifice defined by an annular flow passage in fluid communication with the chamber.
- a valve member is movable between closed and open positions for controlling the flow of fluid from the chamber, through the annular flow passage, and into the exhaust stream.
- the annular flow chamber is interposed between the chamber and the valve member.
- the valve member can include valve seat formed in an outer surface of the injector that faces the exhaust stream.
- the valve member can include a valve head that is movable between closed and open positions. At its closed position, the valve head blocks fluid flow through annular flow passage. At its open position, the valve head is spaced away from the valve seat in the direction of the exhaust stream to permit fluid flow through the annular flow passage.
- valve member seals the orifice from exhaust gas flow when the valve member is in its closed position.
- FIG. 1 is an exploded perspective view of an injector in accordance with at least one embodiment of the present technology.
- FIG. 2 is an exploded perspective view of a body subassembly from the injector of FIG. 1 .
- FIG. 3 is an exploded perspective view of an armature subassembly from the injector of FIG. 1 .
- FIG. 4 is an exploded perspective view of a valve subassembly from the injector of FIG. 1 .
- FIG. 5A is a cross-sectional view of the valve subassembly along line A-A of FIG. 1 .
- FIG. 5B is a partial perspective view of the valve subassembly.
- FIG. 6 is perspective view of a valve seat in accordance with at least one embodiment of the present technology.
- FIG. 7 is a cross-sectional view of the valve seat along line B-B of FIG. 6 .
- FIG. 8A is a cross-sectional view of the injector of FIG. 1 , showing the injector in its closed position.
- FIG. 8B is a cross-sectional view of the injector of FIG. 1 , showing the injector in its open position.
- FIG. 9 is a cross-sectional view of the injector taken along line C-C of FIG. 8A .
- FIG. 10 is an enlarged detail of the injector indicated at D on FIG. 9A
- FIGS. 11A and 11B illustrate a discharge passage and annular flow passage according to certain embodiments of the present technology.
- FIGS. 11C and 11D illustrate a discharge passage and annular flow passage according to certain other embodiments of the present technology.
- FIGS. 11E and 11F illustrate a discharge passage and annular flow passage according to certain other embodiments of the present technology.
- FIGS. 12A-12H is the injector of FIGS. 11A and 11B at various stroke lengths.
- FIG. 13 is a cross-sectional view of an injector according to at least one embodiment of the present technology.
- FIG. 14 is a perspective view illustrating a method for connecting injector of FIG. 12 to an exhaust component.
- FIGS. 15A and 15B are a cross-sectional views of an injector according to at least one embodiment of the present technology.
- FIG. 16 is a schematic of a hydraulic circuit that can be used to supply fluid to an injector in accordance with at least one embodiment of the present technology.
- FIG. 1 is an exploded perspective view of an injector 10 in accordance with at least one embodiment of the present technology.
- the injector 10 can be used, for example, to inject a fluid into the exhaust stream of a diesel engine.
- fluid can include a liquid, gas and/or mixture thereof.
- the fluid can be diesel fuel, which is, for example, injected into the exhaust stream for use in active regeneration of a DPF.
- the fluid can be ammonia or urea, which is injected into the exhaust stream for use in an SCR.
- the injector is described in the context of exhaust aftertreatment, it will be understood and appreciated by those skilled in the art that the injector can be used to inject and/or otherwise dispense one or more fluids in a variety of other environments, including but not limited to dispensing chemicals in chemical applications, preservatives in food, insecticides, pesticides or herbicides in agricultural or other applications, or other fluids capable of being dispensed in the presently described technology; water treatment applications; industrial and/or commercial spraying applications, such as spray drying, spray pyrolysis, and spray freeze drying; fire suppression systems; gas conditioning applications; and humidity control systems and applications.
- the injector 10 generally includes a coil subassembly 12 , a body subassembly 14 , an armature subassembly 16 , a stator 18 and a valve subassembly 20 .
- the injector can also, for example, include a mounting feature for securing the injector to an exhaust component (not shown).
- the mounting feature includes a mounting bracket 13 , a pair of fasteners 15 , such as bolts, and a pair of spacers 17 .
- the spacers 17 include reduced diameter proximal portions 19 that are configured to engage into reciprocal apertures 21 in the mounting bracket 13 .
- the fasteners 15 can be inserted through the spacers 17 .
- the proximal ends of the fasteners 15 extend through the spacers 17 (and the apertures 21 in the mounting bracket 13 ) and can be threaded into reciprocal apertures (not shown) in the exhaust component (not shown) for securing the injector 10 to the exhaust component.
- the coil subassembly 12 further includes a coil 22 wound around a bobbin 24 and a cover 26 that fits over the bobbin 24 .
- the body subassembly 14 includes a main body 28 , a tube 30 and a fitting 32 .
- a longitudinal passage 34 extends through the main body 28 .
- a proximal end 36 of the tube 30 is mounted to a distal end 38 of the main body 28 .
- the tube 30 includes a longitudinal passage 40 that is concentric with the longitudinal passage 34 of the main body 28 .
- the tube 30 is mounted to the main body 28 by inserting the tube 30 into an enlarged diameter counterbore 42 (see FIG. 8A ) formed in the distal end 38 of main body 28 , concentric with the longitudinal passage 34 .
- the fitting 32 mounts on distal end 43 of the tube 30 opposite the main body 28 and includes a longitudinal passage 44 that is concentric with the longitudinal passages 34 , 40 of the main body 28 and the tube 30 .
- the fitting 32 includes a reduced diameter portion 46 that is sized for insertion into the distal end 43 of the tube 30 .
- the main body 28 , tube 30 and fitting 32 can be made of stainless steel, for example, and can be secured together by suitable methods such as threaded connections, press-fitting, welding, brazing or crimping.
- the armature subassembly 16 includes an armature 50 and first and second pins 52 , 54 that extend from opposite ends of the armature.
- the first pin 52 is inserted into a bore 56 in proximal end 58 of the armature 50
- the second pin 54 is inserted into a bore 60 in the distal end 62 of the armature 50 .
- the armature 50 can be formed of a ferromagnetic material such as steel, while the pins can be formed from a non-ferromagnetic material such as stainless steel.
- the pins 52 , 54 can be secured to the armature 50 by suitable methods such as threaded connections, press-fitting, welding, brazing or crimping, for example.
- the armature 50 can include a plurality of flat portions 64 and curved (or radiused) portions 66 extending longitudinally between the proximal and distal ends 58 , 62 of the armature 50 .
- the curved portions 66 allow the armature 50 to freely slide within the tube 30
- the flat portions 64 define fluid passages that allow fluid to flow around the armature 50 .
- the armature 50 can be constructed, for example, by turning a multi-sided piece of bar stock to produce an armature with alternating flat and curved portions 64 , 66 .
- a hexagonal bar stock can be turned to produce an armature with six (6) flat portions and six (6) curved portions.
- the armature 50 can have a circular cross section and one or more flow passages can extend longitudinally through the armature.
- the valve subassembly 20 includes a plunger or pintel 70 , an adapter 72 , a valve body 74 , a bias means, such as a spring 76 , and a retainer 78 .
- the valve body 74 includes a proximal portion 80 that is sized for insertion into a central opening 82 in the adapter 72 .
- the adapter 72 and the proximal portion 80 of the valve body 74 can be directly exposed to the exhaust gases flowing through the exhaust component.
- the adapter 72 and at least the proximal portion 80 of the valve body 74 should be constructed from materials that are suitable for exposure to the elevated temperatures and contaminants within the exhaust stream of an engine, for example.
- the adapter 72 and valve body 74 can be formed from a corrosion resistant material such as stainless steel, for example.
- the adapter 72 and valve body 74 can be secured together by suitable means such as threaded connection, press-fitting, brazing, crimping and/or welding.
- the adapter 72 and valve body 74 are both formed from stainless steel and are brazed together. Heat from the brazing (or from other heat treating process) can be used to heat treat the adapter 72 and the valve body 74 in order to harden these components for wear resistance. Following the brazing/heat treating process, these components can be tempered to make them less brittle.
- a longitudinal passage or bore 84 extends through the valve body 74 's proximal and distal ends 86 , 88 .
- the plunger 70 is sized for insertion into the proximal end of the longitudinal passage 84 .
- Proximal end 90 of the plunger 70 includes a tapered or conical shaped valve head 92 that is configured to mate with a valve seat 94 formed in the proximal end 86 of valve body 74 .
- the interface between the valve head 92 and valve seat 94 forms a seal such as a line seal.
- the distal end 96 of the plunger 70 extends through longitudinal passage 84 beyond the distal end 88 of the valve body 74 .
- the spring 76 mounts concentrically over the distal end 96 of the plunger 70 and is secured in place by the retainer 78 .
- the retainer 78 can be generally disc-shaped and can include a center opening 98 that is configured to mount on a reduced diameter portion 100 of the plunger 70 .
- a slot 102 extends outwardly from the opening 98 on the retainer 78 .
- the spring 76 is then slid over the distal end 96 of the plunger 70 .
- the retainer 78 is then installed by compressing the spring 76 and sliding the retainer 78 laterally (via the slot 102 ) over the reduced diameter portion 100 of the plunger 70 until the center opening 98 is positioned on the reduced diameter portion 100 .
- the spring 76 can be released.
- the force of the spring 76 seats the retainer 78 against an enlarged taper 104 at the distal end of the reduced diameter portion 100 , thereby securing the retainer (and spring) on the plunger 70 .
- the force of the spring 76 against the retainer (and hence the plunger) normally biases the injector 10 to its closed (or seated position).
- the coil 22 can be energized to move the plunger 70 (against the force of the spring 76 ) to an open or unseated position.
- the injector 10 can be assembled by first positioning the mounting bracket 13 on the body subassembly 14 .
- the mounting flange 13 includes an aperture 105 sized to slide over the main body 28 .
- the coil subassembly 12 can be mounted on the body subassembly 14 .
- the bobbin 24 includes a longitudinal passage 105 that is sized to slide over the fitting 32 and the tube 30 .
- the bobbin 24 includes proximal and distal annular flanges 108 , 110 that function to retain the coil 22 on the bobbin 24 .
- the cover 26 can be slid proximally over the bobbin 24 until its proximal end engages with the distal end of the main body 28 .
- the proximal end of the cover 26 is sized to slide over a reduced diameter distal portion 116 of the main body 28 .
- the mounting bracket 13 and bobbin 24 are secured in place between the main body 28 and an inwardly extending annular wall 118 formed at the distal end of the cover 26 .
- the tube 30 projects distally beyond the annular wall 118 .
- a spring clip 122 can be slid over the tube 30 and against the annular wall 118 to secure the coil assembly 12 onto the body subassembly 14 .
- the cover 26 can be secured to the main body 28 by threaded connections, press-fitting, welding, brazing, crimping or other suitable means.
- a pair of electrical conductors 124 e.g., wires, extend from the coil 22 and through the cover 26 for connection to an external electrical circuit (not shown) for energizing/deenergizing the coil 22 to control operation of the injector 10 .
- the injector 10 can include an electrical connector 126 that is configured to mate with a reciprocal electrical connector (not shown) from the external circuit to electrically interconnect the injector and the circuit.
- the armature subassembly 16 can be slid through the distal end of the longitudinal passage 34 in the main body 28 and into the longitudinal passage 40 of the tube 30 .
- the second pin 54 slidably engages with the longitudinal passage 44 in the fitting 32 .
- the stator 18 can be inserted into the longitudinal passage 34 in the main body 28 .
- the first pin 52 of the armature subassembly 16 slidably engages into a longitudinal passage 132 in the stator.
- the interfaces between the first and second pins 52 , 54 and the longitudinal passages 132 , 44 function to center the armature 50 within the tube 30 and facilitate its movement relative thereto.
- the stator 18 includes a distal portion 127 that extends into the proximal end of the tube 30 .
- the stator 18 also includes an annular flange 128 that abuts against a stop 130 formed in the longitudinal passage 34 of the main body 28 . With the stator 18 so installed, the stator 18 and fitting 32 function as proximal and distal stops, respectively, to limit movement of the armature 50 within the tube 30 , and accordingly the stroke of the injector 10 .
- the valve subassembly 20 can be mounted onto the proximal end of the main body 28 .
- the adapter 72 includes and annular flange that is configured to mate with a counterbore 136 formed in the proximal face of the main body 28 concentric with the longitudinal bore 34 .
- the adapter 72 (and hence the valve subassembly 20 ) can be secured to the main body 28 by welding, brazing, crimping, press-fitting, threaded connections, or other suitable means.
- the method of assembly of the injector 10 can be varied and/or modified.
- the order in which the components are assembled can be changed or varied.
- the connections and/or interfaces between the various components can be varied and/or combined.
- the spacers 17 are separately formed from the mounting bracket 13 .
- the spacers 17 can, alternatively, be integrally formed with the mounting bracket 13 .
- the mounting bracket 13 can be integrally formed with another injector component, such as the body subassembly 14 , for example.
- the injector 10 is biased to its closed position as shown in FIG. 8A when the coil 22 is deenergized (i.e., off). Specifically, when the coil 22 is off, the spring 76 biases the plunger 70 proximally relative to the valve body 74 and causes the valve head 92 to seat against the valve seat 94 .
- the injector is normally biased to its open position.
- the injector 10 can be constructed so that the spring 76 normally biases the plunger 70 to its open position and the coil 22 is energized to move, e.g., pull the plunger to its closed position (against the force of the spring).
- the plunger can be integral with, or otherwise connected to, the first pin 52 .
- the injectable fluid e.g., diesel fuel, ammonia or urea
- the injector 10 includes an inlet port 138 and an outlet port 140 that are interconnected by a cooling path (as detailed below).
- the inlet port 138 is formed in the main body 28
- the outlet port 140 is formed in the fitting 32 .
- Fluid flows through the inlet port 138 and into an annular chamber 142 formed between main body 28 , the stator 18 and the valve subassembly 20 . Fluid from the annular chamber 142 flows through a set of first flow passages 144 formed in the valve body 74 (see, e.g., FIGS. 5A , 6 , 7 and 9 ) and into a discharge passage 146 .
- valve subassembly 20 When the valve subassembly 20 is closed, fluid flows through the annular chamber 142 to cool the proximal portion of the plunger 70 (including its valve head 92 ) and the proximal portion of the valve body 74 . Fluid from the annular chamber 142 also flows through a set of second flow passages 148 and into a spring chamber 149 defined by the stator 18 (see, e.g., FIGS. 6 and 10 ). At least one flow passage 150 extends through the distal end of the stator 18 and interconnects the spring chamber 149 with the interior of the tube 30 .
- the spring 76 biases the injector to its closed position, i.e., the valve head 92 is seated against the valve seat 94 .
- the plunger 70 acts against the first pin 52 moving the armature 50 distally (e.g., to the right in FIG. 8A ) in the tube 30 and away from the distal face of the stator 18 .
- the armature 50 is disengaged from the stator 18 (as shown in FIG. 8A )
- fluid flows from spring chamber 149 through the flow passage 150 and into the tube 30 . The fluid then flows distally around the armature 50 (through the flow passages defined by the flat portions 64 ).
- the fitting 32 includes lateral flow passages 152 that intersect with the longitudinal passage 44 . Fluid flows from the tube 30 , into the lateral flow passages 152 , through the longitudinal passage 44 and out of the injector through the outlet port 140 .
- the fitting 32 can include an orifice 154 in the longitudinal passage 44 for controlling the rate of fluid flow through the injector's cooling path.
- the orifice 154 is formed separately from the fitting 32 and is configured to mount in, e.g., thread into, the longitudinal passage 44 . By forming the orifice 154 separately from the fitting 32 , the flow rate can be adjusted by placing different orifices in the fitting. Alternatively, the orifice 154 can be integrally formed with the fitting.
- the fluid then flows distally around the armature 52 (through the flow passages defined by the flat portions 64 ), into the lateral passages 152 , through the longitudinal passage 44 (and orifice 154 ) and out of the injector 10 through the outlet port 140 .
- the flow of fluid e.g. diesel fuel
- the flow of fluid cools the proximal components of the injector (e.g., plunger, valve body, spring, or adapter among others), which helps, fore example, prevent soot accumulation and maintains the desired performance characteristics of the injector's components.
- the injector 10 When the injector 10 is moved to its open position i.e., the valve head 92 is unseated from valve seat 94 (see FIG. 8B ), by energizing the coil 22 .
- the coil 22 When the coil 22 is energized, the flux path created by the coil acts on the armature 50 to move it proximally (e.g., to the left in FIG. 8B ) within the tube 30 .
- the armature 50 moves proximally in the tube, the first pin 52 pushes against the plunger 70 (and against the force of the spring 76 ) to unseat the valve head 92 from the valve seat 94 .
- valve head 92 When the valve head 92 unseats from the valve seat 94 , fluid flows from the discharge passage 146 , through a discharge or metering orifice 159 (see, e.g., FIG. 11A ), out through the gap between the valve head 92 and the valve seat 94 , and into the exhaust stream.
- the use of an outwardly moving (or opening) plunger 70 beneficially functions to reduce soot build up on the injector tip.
- the outward movement of the valve head 92 relative to the valve body 74 tends to dislodge soot that would otherwise accumulate at the junction between the valve head 92 and the valve seat 94 .
- the cooling path can be closed or otherwise modified when the injector is opened.
- the injector when the injector is open, the armature 50 seats against the distal face of the stator 18 to close the flow passage 150 . Closing the cooling flow passage to prevent flow out of the fitting 32 can be beneficial, for example, when there is limited flow and/or pressure available from the external fluid source, e.g., from a supply pump. Further, when the injector 10 is open, the fluid that is ejected from the valve subassembly 20 cools the proximal components.
- the discharge passage 146 is defined by the volume bounded by the wall 164 of longitudinal passage 84 in the valve body 74 and a reduced diameter portion 172 of the plunger 70 .
- fluid flows from the annular chamber 142 and into the discharge passage 146 through the flow passages 144 in the valve body 74 .
- Flow passages according to at least one embodiment of the present disclosure are shown in FIGS. 7 and 9 .
- the flow passages 144 can be axially offset from the longitudinal passage 84 of the valve body 74 . Offsetting the flow passages 144 in the manner shown creates a swirling flow of fluid within the discharge passage 146 .
- This swirling flow provides, for example, even fluid distribution and balances the pressure within the discharge passage 146 .
- the inner ends 147 of the flow passages 144 can be radiused (as shown) to increase flow efficiency and performance. While the illustrated embodiment includes six flow (or swirl) passages 144 , it will be appreciated that the number of passages can be varied.
- the flow passages 144 all have a uniform offset from the longitudinal passage 84 , it should be appreciated that the passages can have no offsets, uniform offsets, varying offsets, and/or combinations thereof.
- the metering orifice 159 is formed by a passage that controls the flow rate between the discharge passage 146 and the passage bounded by the valve head 92 and the valve seat 94 . Moreover, in some embodiments, the metering orifice 159 is defined by an annular flow passage 160 at this location.
- FIGS. 11A and 11B illustrate an annular flow passage 160 according to some embodiments of the present technology. In these embodiments, the annular flow passage 160 is defined by an annular gap between an annular flange 162 on the plunger 70 and the wall 164 of the longitudinal passage 84 in the valve body 74 .
- the plunger 70 can include an annular groove 184 adjacent to the valve head 92 .
- the groove 184 can function to increase the volume downstream of the annular flow passage 160 , thereby increasing the pressure drop across the flow passage 160 and increasing exit velocity.
- the center section of the plunger includes a bearing surface 155 . It will be noted that it is desirable to have a tight clearance between this bearing surface and the wall of the passage 84 to ensure centering of the plunger within the passage 84 . As can be seen in FIGS. 11A and 11B , a relatively larger clearance can be provided between the plunger 70 and the wall of the passage 84 in the region defining the annular flow passage 160 .
- FIGS. 11C and 11D illustrate a discharge passage 146 and annular flow passage 160 according to certain other embodiments of the present technology.
- the longitudinal passage 84 in the valve body 74 includes an increased diameter portion 168 in its proximal end, while the plunger 70 has a generally constant diameter, except for an increased diameter portion 170 at its proximal end adjacent to the valve head 92 .
- the plunger 70 can include an annular groove adjacent to the valve head 92 to increase the volume downstream of the annular flow passage 160 , thereby increasing the pressure drop across the flow passage 160 and increasing exit velocity.
- the discharge passage 146 is defined by the space between the constant diameter portion 173 of the plunger 70 and the increased diameter portion 168 of the longitudinal passage 84 .
- the constant diameter portion 173 of the plunger 70 can also function as a bearing surface 155 in the manner described above.
- the annular flow passage 160 is defined by the annular gap between the increased diameter portion 170 of the plunger 72 and the increased diameter portion 168 of the longitudinal passage 84 .
- FIGS. 11E and 11F illustrate a discharge passage 146 and annular flow passage 160 according to certain other embodiments of the present technology.
- the plunger 70 can exhibit a generally constant diameter along its length except for the valve head 92 .
- the plunger 70 can include an annular groove 184 adjacent to the valve head 92 to increase the exit velocity in the manner discussed above.
- the longitudinal passage 84 in the valve body 74 can exhibit a generally constant diameter, except for an increased diameter interior portion 180 .
- the discharge passage 146 is defined by the annular space between the plunger 70 and the increased diameter inner portion 180 of the passage 84 .
- the annular flow passage 160 is defined by the annular gap between the plunger 70 and the portion 182 of the longitudinal passage 84 that is located proximal to (i.e., outwardly from) the increased diameter interior portion 180 .
- a portion of the plunger 70 can also function as a bearing surface 155 in the manner described above in to ensure centering of the plunger within the passage 84 . Accordingly, it is desirable to have a tight clearance between this bearing surface 155 and the portion 187 of the passage 182 that interfaces with the bearing surface. Further, as can be seen in FIGS. 11E and 11F , a relatively larger clearance can be provided between the plunger 70 and the wall of the passage 84 in the portion 182 of the passage 84 defining the annular flow passage 160 .
- the discharge passage 146 and metering orifice 159 can be sized and configured in accordance with the desired performance characteristics or desired applications and/or environments.
- a relatively small discharge passage 146 can act as a flow restrictor on the orifice 159 .
- the cross-sectional area of the discharge passage is smaller than that of the metering orifice 160 , e.g., annular flow passage 160 , the discharge passage 146 will restrict the maximum flow rater through the orifice 159 .
- increasing the size of the discharge passage 146 increases volume of fluid that is stored in the discharge passage when the injector 10 is closed.
- an increased volume of stored fluid can increase the momentum, e.g., by the fluid from the external fluid source, required to initiate injection.
- the discharge passage 146 can be sized and configured so that it does not restrict fluid flow through the metering orifice 159 , while still providing adequate control over the start of injection. It may be desirable to provide a volume for the passage 146 such that all of the volume of passage 146 is purged each cycle/operation of the device, to assure that no fluid remains in passage 146 from one cycle to the next to reduce the potential for formation of deposits in passage 146 associated with the high heat exposure of the fluid residing within passage 146 . It may also be desirable to provide passage 146 with a small volume to reduce or minimize loss of angular momentum of the fluid between the swirl plate and the annular orifice 160 .
- a relatively high exit velocity from the annular flow passage 160 is beneficial for better fuel atomization.
- the injector 10 can be configured to maximize the velocity of fluid exiting the annular flow passage 160 .
- the exit velocity from the annular flow passage 160 can be increased by increasing the pressure drop across the annular flow passage 160 .
- the exit velocity from the annular orifice 160 is increased by increasing the pressure drop across the annular flow passage 160 .
- One way to increase this pressure drop is by increasing the pressure in discharge passage 146 , which can be accomplished by reducing flow restrictions upstream of the discharge passage. Accordingly, in some embodiments, the pressure in the discharge passage 146 is maximized by minimizing upstream flow restrictions.
- the pressure drop across the annular flow passage 160 can also be increased by reducing the length of the annular flow passage.
- decreasing the length of the annular flow passage 160 tends to increase exit velocity, it can also make the injector more sensitive to manufacturing tolerances. Accordingly, in some embodiments, the length of the annular flow passage 160 is minimized, within the constraints of manufacturing tolerances, in order to increase exit velocity from the flow passage.
- the cross-sectional area and length of the annular flow passage 160 can be empirically determined during design and manufacture in order to provide the desired injection characteristics, including, for example, injection flow rate and distribution.
- increasing the annular cross-sectional area of the flow passage 160 will generally increase fluid flow fluid flow, but will also tend to decrease the velocity of fluid flow.
- the length of the annular flow passage 160 can be empirically determined during design and manufacture in order to provide the desired injection characteristics.
- the longitudinal passage 84 in the valve body 74 has a constant diameter (at least in the region that defines the annular flow passage 160 ).
- the length of the annular flange 162 on the plunger 72 can set the length of the annular flow passage 160 .
- the annular flange 162 can be sized (e.g., its length can be set) such that the stroke (i.e., normal operating range) of the injector 10 can vary without causing any significant change in the performance, e.g., spray uniformity and distribution, of the injector.
- the cross-sectional area of the annular flow passage 160 is generally constant over the normal operating range of the injector.
- FIGS. 12A-12H illustrate the operation of an injector having an annular flow passage 160 constructed in accordance with the embodiments of FIGS. 11A-B .
- the stroke length or lift e.g., the distance the plunger moves proximally from its closed position, continually increase between FIGS. 12A and 12H .
- the annular gap 200 between the valve head 92 and the valve seat 94 increases. If the stroke length is too short, the gap 200 can restrict fluid flow through the annular flow passage 160 (or orifice). (See, e.g., FIG. 12A ).
- the stroke is set so that when the injector is fully open the cross-sectional area of the gap 200 is larger than that of the annular flow passage 160 .
- the length of the annular flow passage 160 can be decreased to increase the velocity of fluid flow through the passage 160 .
- increase fluid velocity through the passage 160 can provide increased atomization of the fluid that is discharged from the injector.
- the length of the annular flow passage 160 can be controlled by the stroke of the plunger 70 . In particular, this length decreases as stroke length increases. At some point, the length of the flow passage 160 can become too short to provide good flow control and characteristics from the annular flow passage 160 . In particular, as this length of the passage 160 decreases, the ability to maintain a constant cross sectional area for the annular flow passage can become more sensitive to manufacturing tolerances.
- the performance, e.g., flow rate, of the injector may begin to fluctuate with stroke length.
- the distal end of the annular flange 162 moves proximally past junction of the valve seat 94 and the passage 84 , the cross-sectional area will continue to increase with increasing outward movement of the plunger. Accordingly, in some embodiments, the length of the annular flow passage is minimized, within manufacturing tolerances, while the cross-sectional area of the flow passage is held constant.
- the stroke length and annular flow passage 160 can be set, e.g., through empirical testing during design and manufacture, in order to provide the desired injector operating characteristics.
- proportional control can be used to provide variable flow from the injector.
- proportional control can be used to adjust the stroke length (i.e., plunger lift) and accordingly the length of the annular flow passage 160 .
- the annular flow passage 160 is located inwardly from the valve seat 94 . Accordingly, when the injector 10 is closed, the annular flow passage 160 is protected from exposure to the exhaust stream by the seal between the valve head 92 and the valve seat 94 , thereby reducing, for example, soot accumulation and injector fouling. Injector fouling is further reduced because fluid flows out of the annular flow passage 160 whenever the plunger 70 is open. This constant outward fluid flow prevents contaminates from entering and/or flushes contaminants form the injector, thereby reducing injector fouling.
- FIG. 13 illustrates a water-cooled injector 1010 according to at least one embodiment of the present technology.
- the injector 1010 includes many components that are the same or similar to those used in the injector 10 of FIG. 1 .
- the injector 1010 uses a cooling fluid, such as water, instead of the injectable fluid, e.g., diesel fuel, to cool the injector components.
- the injector 1010 includes a cooling flange 1300 mounted on the proximal end of the injector.
- the cooling flange 1300 circulates cooling fluid around the injector components that are adjacent or near the flow of exhaust gas in order to cool these components.
- the injector 1010 includes a coil subassembly 1012 , a body subassembly 1014 , an armature subassembly 1016 and a valve subassembly 1020 .
- the coil subassembly 1012 includes a coil 1022 wound on a bobbin 1024 and a cover 1025 for securing the coil in place on the bobbin.
- the body subassembly 1014 includes a main body 1028 , a tube 1030 and a fitting 1032 . The proximal end of the tube 1030 is secured to the distal end of the main body 1028 .
- the proximal end of the tube 1030 is mounted over an annular protrusion 1035 that extends from the distal end of the main body 1028 .
- the fitting 1032 mounts to the distal end of the tube 1030 opposite the main body 1028 .
- the fitting 1032 includes a reduced diameter portion 1046 that is sized for insertion into the distal end of the tube 1030 .
- the main body 1028 , tube 1030 and fitting 1032 can be made of stainless steel, for example, and can be secured together by suitable methods such as threaded connections, press-fitting, welding, brazing or crimping, among others.
- the armature subassembly 1016 includes an armature 1050 and a pin 1051 .
- the pin 1051 is mounted through a longitudinal passage in armature 1050 .
- the pin 1051 may be secured to the armature 1050 by welding, brazing, press-fitting or other suitable means, for example.
- a first portion 1052 of the pin 1051 extends proximally from the armature 1050 and slidably engages with a longitudinal passage 1053 in the distal end of the main body 1028 .
- a second portion 1054 of the pin 1051 extends distally in a counterbore 1055 formed in the distal portion of the armature 1050 and slidably engages into a longitudinal bore 1059 in the proximal end of the fitting 1032 .
- the armature 50 in the injector 10 includes flow passages that are defined by flat portions 64 on the periphery of the armature 50 . Since the injector 1010 does not include an internal cooling path for the injectable fluid, for example, diesel fuel, flow passages are not provided in the armature 1050 . Accordingly, the armature 1050 may, for example, have a circular cross-section.
- the valve subassembly 1020 can have similar construction and operation as the valve assembly 20 described above.
- the valve subassembly 1020 includes a plunger 1070 , an adapter 1072 , a valve body 1074 , a spring 1076 and a spring retainer 1078 .
- the injector 1010 includes an inlet port 1138 for supplying a fluid, e.g., diesel fuel, to the injector from an external source (not shown).
- the fluid flows through the inlet port 1138 and into a main chamber 1139 formed between main body 1028 and the valve subassembly 1020 . Fluid from the main chamber 1139 flows through a plurality of flow passages (not shown) in the valve body 1074 and into a discharge passage (not shown).
- the flow passages in the valve body 1074 and the discharge passage can have the same general construction as the flow passages 144 and discharge passage 146 that were described above in connection with the injector 10 .
- the flow passages can be axially offset, as described above, to create a swirling flow of fluid within the discharge passage 1146 .
- the injector 1010 When the coil 1022 is deenergized, the injector 1010 is biased to its closed position by the spring 1076 . The injector 1010 is moved to its open position by energizing the coil 1022 .
- the flux path created by the coil 1022 acts on the armature 1050 to move the armature proximally (e.g., to the left in FIG. 13 ) within the tube 1030 .
- the pin 1051 pushes against the plunger 1070 (and against the force of the spring 1076 ) to unseat valve head 1092 from valve seat 1094 .
- the annular flow passage 1160 can have the same general construction and operation as the annular flow passage 160 described above in connection with the injector 10 .
- the injector 1010 When the injector 1010 is connected to an exhaust component, components on the proximal end, including the valve head 1092 and valve seat 1094 , will typically be exposed directly to the exhaust gases flowing through the exhaust component.
- the injector 1010 includes a cooling flange 1300 that circulates cooling fluid around the injector components that are adjacent or near the flow of exhaust gas in order to cool these components.
- the cooling flange 1300 includes a longitudinal passage 1310 configured to receive the proximal portion of the main body 1028 .
- the main body 1028 and longitudinal passage 1310 include reciprocal threads 1312 for securing the injector 1010 to the cooling flange 1300 .
- the main body 1028 can be secured to the cooling flange 1300 by welding, brazing, crimping, press-fitting or other suitable means.
- the cooling flange 1300 also includes an annular counterbore 1313 formed in its proximal face outwardly from and concentrically with the longitudinal passage 1310 .
- An end cap 1314 is mounted on proximal end of the cooling flange 1300 to seal off the counterbore 1313 and define a cooling chamber 1316 .
- the end cap 1314 can be secured in place by suitable means such as brazing, crimping, welding, press-fitting or threaded connection.
- the flange 1300 includes an inlet port 1320 and outlet port 1322 that are fluidly connected to the cooling chamber through longitudinal flow passages 1323 formed in the cooling flange 1300 .
- the inlet and outlet ports can be connected to an external source (not shown) for circulating cooling fluid through the cooling chamber 1316 in order to cool the proximal end of the injector 1010 .
- the injector 1010 can be mounted to an exhaust component 1330 for injecting a fluid, such as diesel fuel, into an exhaust stream flowing through a passage 1332 in the exhaust component.
- the injector 1010 includes mounting features configured to mate with reciprocal mounting features on the exhaust component 1330 .
- the mounting features include mounting apertures 1334 on the injector 1010 that align with reciprocal apertures 1336 on the exhaust component.
- Fasteners such as bolts 1338 , extend through the apertures 1134 in the injector 1010 and thread into the apertures 1136 in the exhaust component 1330 to secure the injector to the exhaust component.
- Spacers 1342 can be positioned on the fasteners 1338 before the fasteners are installed. The spacers 1342 can help dissipate from the injector.
- a gasket 1340 can be interposed between the injector 1010 and the exhaust component 1330 to seal against gas leaks.
- FIGS. 15A and 15B illustrate another water-cooled injector 1010 B according to at least one embodiment of the present technology.
- the injector 1010 B includes many components that are the same or similar to those used in the injector 1010 of FIG. 13 . Accordingly, like reference numerals are used to identify like components and only the primary differences between the injectors 1010 and 1010 B will be described.
- One difference the cooling flange and main body of the injector 1010 B are integrally formed with one another. This composite structure is identified with reference number 1350 in FIG. 11B .
- the injector 1010 B has a different path for fluid flow through the injector.
- the fluid inlet 1138 B is formed in the distal end of the fitting 1032 B. Fluid from the inlet 1138 B flows into a longitudinal passage 1354 in the fitting. Fluid then flows into the tube 1030 and through a longitudinal passage 1354 in the armature 1050 B.
- a pin 1052 B extends from the proximal end of the armature 1050 and engages against the distal end of the plunger 1070 .
- the pin 1052 B includes a longitudinal passage 1354 that is in fluid communication with the longitudinal passage 1354 of the armature 1350 . Outlets 1358 in the proximal end of the passage open into the main chamber 1039 B.
- the flow passages in the valve body 1074 and the discharge passage can have the same general construction as the flow passages 144 and discharge passage 146 that were described above in connection with the injector 10 .
- the flow passages can be axially offset, as described above, to create a swirling flow of fluid within the discharge passage 1146 .
- the injector 1010 is moved to its open position (see FIG. 15B ) by energizing the coil 1022 .
- the flux path created by the coil 1022 acts on the armature 1050 to move the armature proximally (e.g., to the left in FIG. 15B ) within the tube 1030 .
- the pin 1050 B pushes against the plunger 1070 (and against the force of the spring 1076 ) to unseat valve head 1092 from valve seat 1094 .
- the annular flow passage can have the same general construction and operation as the annular flow passage 160 described above in connection with the injector 10 .
- FIG. 16 illustrates a hydraulic circuit 1600 that can be used to supply fluid to an injector 1602 according to certain embodiments of the present technology.
- the hydraulic circuit 1600 can include a fluid supply 1604 that delivers pressurized fluid to the inlet of the injector 1602 through a control manifold 1606 .
- the fluid supply 1602 can include a tank 1610 and a pump 1612 .
- the inlet of the pump 1612 can be fluidly connected to the tank 1610 through a filter 1618 .
- the control manifold 1606 can include control valve 1614 that is moveable between open and closed positions. According to at least some embodiments the control valve can be a solenoid-operated valve.
- the inlet of the control valve 1614 can be fluidly connected to the pump 1612 through the filter 1618 , while the outlet of the control valve can be connected to the inlet port of the injector 1602 .
- the control valve 1614 is normally biased closed for fail-safe conditions.
- the control valve 1614 can be maintained in its open position, e.g., by the solenoid, to allow pressurized fluid to be supplied from the pump to the injector.
- An electronic controller (not shown) can be used to selectively energize the injector 1602 to inject fluid into an exhaust gas stream, for example.
- the injector 1602 includes a cooling flow path such as described in connection with the injector 10 of FIG.
- the hydraulic circuit 1600 can include a return flow line 1622 from the injector 1602 and the tank 1610 . Accordingly, when the injector 1602 is closed, fluid can be pumped from the tank 1610 through the injector 1602 and back to the tank through the return line to cool the injector in the manner described above.
- the return flow line 1622 can include a pressure relief valve to maintain the pressure at the injector 1602 above a minimum threshold pressure when the control valve 1614 is closed.
- the control manifold 1606 can include a pressure sensor 1620 for monitoring the fluid pressure between the control valve 1614 and the injector 1602 .
- the pressure sensor 1620 can be used to control dosing from the fluid injector.
- look-up table can be developed to correlate inlet pressure to dosing rates, e.g., fluid flow rates, from the injector.
- an electronic control unit can determine the flow rate from the injector and can in turn be used to control the operation of the fluid injector.
- the pressure sensor can also be used for on board diagnostics, including, for example, detecting leaks in the hydraulic circuit and failure of the control valve. For example, when the control valve is commanded to be open, an absence of pressure can indicate failure of the control valve. A fluid leak can be detected by activating the pump 1612 , and thereafter closing the control valve 1614 while monitoring the pressure sensor detected by the pressure sensor. A decreasing pressure reading under these conditions can indicate a fluid leak between the control valve 1614 and the injector 1602 .
Abstract
An injector for controllably injecting a fluid into an exhaust stream having a housing that defines a chamber for storing the fluid and a metering orifice defined by an annular flow passage in fluid communication with the chamber. A valve member is movable between closed and open positions for controlling the flow of fluid from the chamber, through the annular flow passage, and into the exhaust stream.
Description
- This application claims priority to U.S. Application Ser. No. 61/691,495, having a filing date of Aug. 21, 2012, the disclosure of which is incorporated herein by reference in its entirety.
- Emission standards around the world continue to place stricter limits on emissions from diesel engines, particularly those in over-the-road vehicles, such as trucks. In order to provide consumers with engines that comply with these standards, manufacturers often employ after-treatment systems that are configured to capture pollutants and/or convert them into acceptable emission constituents.
- For example, diesel particulate filters (DPFs) are commonly used to remove particulate matter, e.g., soot, from engine exhaust flow. A DPF has a structure that permits exhaust gases to flow through the filter while trapping solid particulate matter. Over time, the accumulated particulate matter can reduce the efficiency of the filter. Accordingly, various methods are used to clean or “regenerate” the filter to its original state by burning off the trapped particulate matter.
- One method for cleaning the DPF is referred to as “active regeneration.” In active regeneration, the exhaust gas temperature is increased to levels to “burn off” the accumulated particulate matter in the DPF. For example, an injector (commonly referred to as “closer”) can be used to periodically inject diesel fuel (or other reagent) into the engine exhaust upstream of the DPF. The injected fuel is burned to raise the temperature of the exhaust gas entering the DPF to a level sufficient to burn off the accumulated soot. In some systems, the elevated temperature of the exhaust gas entering the DPF may be generated in a diesel oxidation catalyst (DOC) located upstream of the DPF. The doser injects fuel exhaust stream upstream of the DOC. The DOC consumes the fuel, resulting in an exothermic reaction in the DOC, which elevates the temperature of the exhaust gas flowing downstream to the DPF to approximately and/or above 550° C., causing the “burn off” event and DPF regeneration.
- Similarly, selective catalytic reduction (SCR) can be used to reduce NOx emissions from diesel engines, for example. SCR involves injecting an atomized reagent, such as ammonia or urea, into the engine exhaust stream. The reagent/exhaust gas mixture is passed through a catalyst, which reduces NOx concentration in the presence of the reagent.
- Injectors that are used for DPF regeneration and SCR typically inject the reagent directly into the engine exhaust flow. As such, these injectors can be exposed to harsh operating conditions, including elevated temperatures and contaminants within the exhaust stream. In such an environment, soot can accumulate in and around the tip of the injector. With time, the soot build up can lead to a reduced flow through the injector, poor atomization, or even a complete loss of flow if the injector becomes completely covered, or plugged. This phenomena is commonly referred to in the art as “injector fouling.”
- Embodiments depicted herein disclose an injector for injecting fluid, such as diesel fuel, ammonia, urea or other reagent, into an engine exhaust stream while reducing the occurrence of injector fouling.
- In at least one aspect, the presently described technology involves an injector for controllably injecting a fluid into an exhaust stream having a housing that defines a chamber for storing the fluid and an orifice defined by an annular flow passage in fluid communication with the chamber. A valve member is movable between closed and open positions for controlling the flow of fluid from the chamber, through the annular flow passage, and into the exhaust stream. In some embodiments and at lest one aspect of the present technology, the annular flow chamber is interposed between the chamber and the valve member.
- According to further embodiments, the valve member can include valve seat formed in an outer surface of the injector that faces the exhaust stream. The valve member can include a valve head that is movable between closed and open positions. At its closed position, the valve head blocks fluid flow through annular flow passage. At its open position, the valve head is spaced away from the valve seat in the direction of the exhaust stream to permit fluid flow through the annular flow passage.
- In still further embodiments, the valve member seals the orifice from exhaust gas flow when the valve member is in its closed position.
-
FIG. 1 is an exploded perspective view of an injector in accordance with at least one embodiment of the present technology. -
FIG. 2 is an exploded perspective view of a body subassembly from the injector ofFIG. 1 . -
FIG. 3 is an exploded perspective view of an armature subassembly from the injector ofFIG. 1 . -
FIG. 4 is an exploded perspective view of a valve subassembly from the injector ofFIG. 1 . -
FIG. 5A is a cross-sectional view of the valve subassembly along line A-A ofFIG. 1 . -
FIG. 5B is a partial perspective view of the valve subassembly. -
FIG. 6 is perspective view of a valve seat in accordance with at least one embodiment of the present technology. -
FIG. 7 is a cross-sectional view of the valve seat along line B-B ofFIG. 6 . -
FIG. 8A is a cross-sectional view of the injector ofFIG. 1 , showing the injector in its closed position. -
FIG. 8B is a cross-sectional view of the injector ofFIG. 1 , showing the injector in its open position. -
FIG. 9 is a cross-sectional view of the injector taken along line C-C ofFIG. 8A . -
FIG. 10 is an enlarged detail of the injector indicated at D onFIG. 9A -
FIGS. 11A and 11B illustrate a discharge passage and annular flow passage according to certain embodiments of the present technology. -
FIGS. 11C and 11D illustrate a discharge passage and annular flow passage according to certain other embodiments of the present technology. -
FIGS. 11E and 11F illustrate a discharge passage and annular flow passage according to certain other embodiments of the present technology. -
FIGS. 12A-12H is the injector ofFIGS. 11A and 11B at various stroke lengths. -
FIG. 13 is a cross-sectional view of an injector according to at least one embodiment of the present technology. -
FIG. 14 is a perspective view illustrating a method for connecting injector ofFIG. 12 to an exhaust component. -
FIGS. 15A and 15B are a cross-sectional views of an injector according to at least one embodiment of the present technology. -
FIG. 16 is a schematic of a hydraulic circuit that can be used to supply fluid to an injector in accordance with at least one embodiment of the present technology. -
FIG. 1 is an exploded perspective view of an injector 10 in accordance with at least one embodiment of the present technology. The injector 10 can be used, for example, to inject a fluid into the exhaust stream of a diesel engine. In the context of the present technology, fluid can include a liquid, gas and/or mixture thereof. In some embodiments, the fluid can be diesel fuel, which is, for example, injected into the exhaust stream for use in active regeneration of a DPF. In other, embodiments, the fluid can be ammonia or urea, which is injected into the exhaust stream for use in an SCR. While the injector is described in the context of exhaust aftertreatment, it will be understood and appreciated by those skilled in the art that the injector can be used to inject and/or otherwise dispense one or more fluids in a variety of other environments, including but not limited to dispensing chemicals in chemical applications, preservatives in food, insecticides, pesticides or herbicides in agricultural or other applications, or other fluids capable of being dispensed in the presently described technology; water treatment applications; industrial and/or commercial spraying applications, such as spray drying, spray pyrolysis, and spray freeze drying; fire suppression systems; gas conditioning applications; and humidity control systems and applications. - The injector 10 generally includes a coil subassembly 12, a
body subassembly 14, anarmature subassembly 16, astator 18 and avalve subassembly 20. The injector can also, for example, include a mounting feature for securing the injector to an exhaust component (not shown). According to at least one embodiment, the mounting feature includes a mountingbracket 13, a pair offasteners 15, such as bolts, and a pair ofspacers 17. Thespacers 17 include reduced diameterproximal portions 19 that are configured to engage intoreciprocal apertures 21 in the mountingbracket 13. With thespacers 17 so installed in the mountingbracket 13, thefasteners 15 can be inserted through thespacers 17. The proximal ends of thefasteners 15 extend through the spacers 17 (and theapertures 21 in the mounting bracket 13) and can be threaded into reciprocal apertures (not shown) in the exhaust component (not shown) for securing the injector 10 to the exhaust component. - The coil subassembly 12, further includes a
coil 22 wound around abobbin 24 and acover 26 that fits over thebobbin 24. - Referring additionally to
FIG. 2 , thebody subassembly 14 includes amain body 28, atube 30 and a fitting 32. Alongitudinal passage 34 extends through themain body 28. Aproximal end 36 of thetube 30 is mounted to adistal end 38 of themain body 28. Thetube 30 includes alongitudinal passage 40 that is concentric with thelongitudinal passage 34 of themain body 28. In the illustrated embodiment, thetube 30 is mounted to themain body 28 by inserting thetube 30 into an enlarged diameter counterbore 42 (seeFIG. 8A ) formed in thedistal end 38 ofmain body 28, concentric with thelongitudinal passage 34. The fitting 32 mounts ondistal end 43 of thetube 30 opposite themain body 28 and includes alongitudinal passage 44 that is concentric with thelongitudinal passages main body 28 and thetube 30. In the illustrated embodiment, the fitting 32 includes a reduceddiameter portion 46 that is sized for insertion into thedistal end 43 of thetube 30. Themain body 28,tube 30 and fitting 32 can be made of stainless steel, for example, and can be secured together by suitable methods such as threaded connections, press-fitting, welding, brazing or crimping. - Referring additionally to
FIG. 3 , thearmature subassembly 16 includes anarmature 50 and first andsecond pins first pin 52 is inserted into abore 56 inproximal end 58 of thearmature 50, while thesecond pin 54 is inserted into abore 60 in thedistal end 62 of thearmature 50. In some embodiments, thearmature 50 can be formed of a ferromagnetic material such as steel, while the pins can be formed from a non-ferromagnetic material such as stainless steel. Thepins armature 50 by suitable methods such as threaded connections, press-fitting, welding, brazing or crimping, for example. Thearmature 50 can include a plurality offlat portions 64 and curved (or radiused)portions 66 extending longitudinally between the proximal and distal ends 58, 62 of thearmature 50. As discussed in greater detail below, thecurved portions 66 allow thearmature 50 to freely slide within thetube 30, while theflat portions 64 define fluid passages that allow fluid to flow around thearmature 50. Thearmature 50 can be constructed, for example, by turning a multi-sided piece of bar stock to produce an armature with alternating flat andcurved portions armature 50 can have a circular cross section and one or more flow passages can extend longitudinally through the armature. - Referring now to
FIGS. 4-7 , thevalve subassembly 20 includes a plunger orpintel 70, anadapter 72, avalve body 74, a bias means, such as aspring 76, and aretainer 78. Thevalve body 74 includes aproximal portion 80 that is sized for insertion into acentral opening 82 in theadapter 72. When the injector 10 is connected to an exhaust component, theadapter 72 and theproximal portion 80 of thevalve body 74 can be be directly exposed to the exhaust gases flowing through the exhaust component. Accordingly, theadapter 72 and at least theproximal portion 80 of thevalve body 74 should be constructed from materials that are suitable for exposure to the elevated temperatures and contaminants within the exhaust stream of an engine, for example. In this regard, theadapter 72 andvalve body 74 can be formed from a corrosion resistant material such as stainless steel, for example. Theadapter 72 andvalve body 74 can be secured together by suitable means such as threaded connection, press-fitting, brazing, crimping and/or welding. According to at least one embodiment, theadapter 72 andvalve body 74 are both formed from stainless steel and are brazed together. Heat from the brazing (or from other heat treating process) can be used to heat treat theadapter 72 and thevalve body 74 in order to harden these components for wear resistance. Following the brazing/heat treating process, these components can be tempered to make them less brittle. - A longitudinal passage or bore 84 extends through the
valve body 74's proximal and distal ends 86, 88. Theplunger 70 is sized for insertion into the proximal end of thelongitudinal passage 84.Proximal end 90 of theplunger 70 includes a tapered or conical shapedvalve head 92 that is configured to mate with avalve seat 94 formed in theproximal end 86 ofvalve body 74. The interface between thevalve head 92 andvalve seat 94 forms a seal such as a line seal. Thedistal end 96 of theplunger 70 extends throughlongitudinal passage 84 beyond thedistal end 88 of thevalve body 74. - The
spring 76 mounts concentrically over thedistal end 96 of theplunger 70 and is secured in place by theretainer 78. According to at least one embodiment, theretainer 78 can be generally disc-shaped and can include acenter opening 98 that is configured to mount on a reduceddiameter portion 100 of theplunger 70. As can be seen inFIG. 5B , aslot 102 extends outwardly from theopening 98 on theretainer 78. During assembly, theplunger 70 is inserted distally throughlongitudinal passage 84 until thevalve head 92 abuts thevalve seat 94. In some embodiments, the center section of the plunger defines a bearing surface 155 (seeFIG. 4 ) that forms a close, free-sliding fit with thelongitudinal passage 84. It will be noted that it is desirable to have a relatively small (or tight) clearance between this bearingsurface 155 and the wall of thepassage 84 to center the plunger within thepassage 84. - The
spring 76 is then slid over thedistal end 96 of theplunger 70. Theretainer 78 is then installed by compressing thespring 76 and sliding theretainer 78 laterally (via the slot 102) over the reduceddiameter portion 100 of theplunger 70 until thecenter opening 98 is positioned on the reduceddiameter portion 100. When theretainer 78 is properly positioned, thespring 76 can be released. The force of thespring 76 seats theretainer 78 against anenlarged taper 104 at the distal end of the reduceddiameter portion 100, thereby securing the retainer (and spring) on theplunger 70. The force of thespring 76 against the retainer (and hence the plunger) normally biases the injector 10 to its closed (or seated position). As explained below, thecoil 22 can be energized to move the plunger 70 (against the force of the spring 76) to an open or unseated position. - Referring again to
FIG. 1 and also toFIGS. 8A and 8B , the injector 10 can be assembled by first positioning the mountingbracket 13 on thebody subassembly 14. For this purpose, the mountingflange 13 includes anaperture 105 sized to slide over themain body 28. - Once the mounting
bracket 13 is positioned on themain body 28, the coil subassembly 12 can be mounted on thebody subassembly 14. To this end, thebobbin 24 includes alongitudinal passage 105 that is sized to slide over the fitting 32 and thetube 30. Thebobbin 24 includes proximal and distal annular flanges 108, 110 that function to retain thecoil 22 on thebobbin 24. Once thebobbin 24 is in place on thetube 30, thecover 26 can be slid proximally over thebobbin 24 until its proximal end engages with the distal end of themain body 28. In the illustrate embodiment, the proximal end of thecover 26 is sized to slide over a reduced diameterdistal portion 116 of themain body 28. As can be seen inFIG. 8A , when thecover 26 is so mounted on thebody subassembly 14, the mountingbracket 13 andbobbin 24 are secured in place between themain body 28 and an inwardly extendingannular wall 118 formed at the distal end of thecover 26. Thetube 30 projects distally beyond theannular wall 118. Aspring clip 122 can be slid over thetube 30 and against theannular wall 118 to secure the coil assembly 12 onto thebody subassembly 14. Alternatively or additionally, thecover 26 can be secured to themain body 28 by threaded connections, press-fitting, welding, brazing, crimping or other suitable means. As can be seen inFIG. 8A , a pair ofelectrical conductors 124, e.g., wires, extend from thecoil 22 and through thecover 26 for connection to an external electrical circuit (not shown) for energizing/deenergizing thecoil 22 to control operation of the injector 10. The injector 10 can include anelectrical connector 126 that is configured to mate with a reciprocal electrical connector (not shown) from the external circuit to electrically interconnect the injector and the circuit. - Once the coil subassembly 12 is mounted on the
body subassembly 14, thearmature subassembly 16 can be slid through the distal end of thelongitudinal passage 34 in themain body 28 and into thelongitudinal passage 40 of thetube 30. As thearmature subassembly 16 slides into thetube 30, thesecond pin 54 slidably engages with thelongitudinal passage 44 in the fitting 32. Once thearmature subassembly 16 is positioned within thetube 30, thestator 18 can be inserted into thelongitudinal passage 34 in themain body 28. As thestator 18 is slide into place, thefirst pin 52 of thearmature subassembly 16 slidably engages into alongitudinal passage 132 in the stator. The interfaces between the first andsecond pins longitudinal passages armature 50 within thetube 30 and facilitate its movement relative thereto. Thestator 18 includes adistal portion 127 that extends into the proximal end of thetube 30. Thestator 18 also includes anannular flange 128 that abuts against astop 130 formed in thelongitudinal passage 34 of themain body 28. With thestator 18 so installed, thestator 18 and fitting 32 function as proximal and distal stops, respectively, to limit movement of thearmature 50 within thetube 30, and accordingly the stroke of the injector 10. - Once the
stator 18 is installed, thevalve subassembly 20 can be mounted onto the proximal end of themain body 28. To this end, theadapter 72 includes and annular flange that is configured to mate with acounterbore 136 formed in the proximal face of themain body 28 concentric with thelongitudinal bore 34. The adapter 72 (and hence the valve subassembly 20) can be secured to themain body 28 by welding, brazing, crimping, press-fitting, threaded connections, or other suitable means. - It will be appreciated by at least those skilled in the relevant art that the method of assembly of the injector 10 can be varied and/or modified. For example, the order in which the components are assembled can be changed or varied. Alternatively or additionally, the connections and/or interfaces between the various components can be varied and/or combined. For example, in the illustrated embodiment, the
spacers 17 are separately formed from the mountingbracket 13. Thespacers 17 can, alternatively, be integrally formed with the mountingbracket 13. Similarly, the mountingbracket 13 can be integrally formed with another injector component, such as thebody subassembly 14, for example. - According to at least some further embodiments of the present technology, the injector 10 is biased to its closed position as shown in
FIG. 8A when thecoil 22 is deenergized (i.e., off). Specifically, when thecoil 22 is off, thespring 76 biases theplunger 70 proximally relative to thevalve body 74 and causes thevalve head 92 to seat against thevalve seat 94. Alternatively, in some embodiments, the injector is normally biased to its open position. For example, the injector 10 can be constructed so that thespring 76 normally biases theplunger 70 to its open position and thecoil 22 is energized to move, e.g., pull the plunger to its closed position (against the force of the spring). In such embodiments, the plunger can be integral with, or otherwise connected to, thefirst pin 52. - According to at least some embodiments, the injectable fluid, e.g., diesel fuel, ammonia or urea, circulates through the injector in order to cool the injector components and particularly components that are adjacent or near the flow of exhaust gas. To that end, the injector 10 includes an
inlet port 138 and anoutlet port 140 that are interconnected by a cooling path (as detailed below). In the illustrated embodiment, theinlet port 138 is formed in themain body 28, while theoutlet port 140 is formed in the fitting 32. Fluid flows through theinlet port 138 and into anannular chamber 142 formed betweenmain body 28, thestator 18 and thevalve subassembly 20. Fluid from theannular chamber 142 flows through a set offirst flow passages 144 formed in the valve body 74 (see, e.g.,FIGS. 5A , 6, 7 and 9) and into adischarge passage 146. - When the
valve subassembly 20 is closed, fluid flows through theannular chamber 142 to cool the proximal portion of the plunger 70 (including its valve head 92) and the proximal portion of thevalve body 74. Fluid from theannular chamber 142 also flows through a set ofsecond flow passages 148 and into aspring chamber 149 defined by the stator 18 (see, e.g.,FIGS. 6 and 10 ). At least oneflow passage 150 extends through the distal end of thestator 18 and interconnects thespring chamber 149 with the interior of thetube 30. When the coil is off (deenergized), thespring 76 biases the injector to its closed position, i.e., thevalve head 92 is seated against thevalve seat 94. When this occurs, theplunger 70 acts against thefirst pin 52 moving thearmature 50 distally (e.g., to the right inFIG. 8A ) in thetube 30 and away from the distal face of thestator 18. When thearmature 50 is disengaged from the stator 18 (as shown inFIG. 8A ), fluid flows fromspring chamber 149 through theflow passage 150 and into thetube 30. The fluid then flows distally around the armature 50 (through the flow passages defined by the flat portions 64). - Additionally, the fitting 32 includes
lateral flow passages 152 that intersect with thelongitudinal passage 44. Fluid flows from thetube 30, into thelateral flow passages 152, through thelongitudinal passage 44 and out of the injector through theoutlet port 140. The fitting 32 can include anorifice 154 in thelongitudinal passage 44 for controlling the rate of fluid flow through the injector's cooling path. In the illustrated embodiment, theorifice 154 is formed separately from the fitting 32 and is configured to mount in, e.g., thread into, thelongitudinal passage 44. By forming theorifice 154 separately from the fitting 32, the flow rate can be adjusted by placing different orifices in the fitting. Alternatively, theorifice 154 can be integrally formed with the fitting. - In sum, when the injector 10 is closed, fluid flows through the
inlet port 138 and into theannular chamber 142. Fluid from theannular chamber 142 flows into the discharge passage 146 (through the first passages 144) and also into the spring chamber 149 (through the second flow passages 148). When the injector 10 is closed, thearmature 50 is biased distally in thetube 30 and out of engagement with the face of thestator 18. As a result, fluid from thespring chamber 149 flows through thelongitudinal passage 150 and into thetube 30. The fluid then flows distally around the armature 52 (through the flow passages defined by the flat portions 64), into thelateral passages 152, through the longitudinal passage 44 (and orifice 154) and out of the injector 10 through theoutlet port 140. The flow of fluid (e.g. diesel fuel) in the manner just described cools the proximal components of the injector (e.g., plunger, valve body, spring, or adapter among others), which helps, fore example, prevent soot accumulation and maintains the desired performance characteristics of the injector's components. - When the injector 10 is moved to its open position i.e., the
valve head 92 is unseated from valve seat 94 (seeFIG. 8B ), by energizing thecoil 22. When thecoil 22 is energized, the flux path created by the coil acts on thearmature 50 to move it proximally (e.g., to the left inFIG. 8B ) within thetube 30. As thearmature 50 moves proximally in the tube, thefirst pin 52 pushes against the plunger 70 (and against the force of the spring 76) to unseat thevalve head 92 from thevalve seat 94. When thevalve head 92 unseats from thevalve seat 94, fluid flows from thedischarge passage 146, through a discharge or metering orifice 159 (see, e.g.,FIG. 11A ), out through the gap between thevalve head 92 and thevalve seat 94, and into the exhaust stream. The use of an outwardly moving (or opening)plunger 70 beneficially functions to reduce soot build up on the injector tip. In particular, the outward movement of thevalve head 92 relative to thevalve body 74 tends to dislodge soot that would otherwise accumulate at the junction between thevalve head 92 and thevalve seat 94. - In some embodiments, the cooling path can be closed or otherwise modified when the injector is opened. For example, in some embodiments, when the injector is open, the
armature 50 seats against the distal face of thestator 18 to close theflow passage 150. Closing the cooling flow passage to prevent flow out of the fitting 32 can be beneficial, for example, when there is limited flow and/or pressure available from the external fluid source, e.g., from a supply pump. Further, when the injector 10 is open, the fluid that is ejected from thevalve subassembly 20 cools the proximal components. - In still further embodiments, the
discharge passage 146 is defined by the volume bounded by thewall 164 oflongitudinal passage 84 in thevalve body 74 and a reduceddiameter portion 172 of theplunger 70. As discussed above, fluid flows from theannular chamber 142 and into thedischarge passage 146 through theflow passages 144 in thevalve body 74. Flow passages according to at least one embodiment of the present disclosure are shown inFIGS. 7 and 9 . As illustrated, theflow passages 144 can be axially offset from thelongitudinal passage 84 of thevalve body 74. Offsetting theflow passages 144 in the manner shown creates a swirling flow of fluid within thedischarge passage 146. This swirling flow provides, for example, even fluid distribution and balances the pressure within thedischarge passage 146. As a result, when the injector opens, fluid from thedischarge passage 146 discharges evenly through themetering orifice 159, resulting in a uniform and well-distributed spray of fluid from the injector. Further, according to some embodiments, the inner ends 147 of theflow passages 144 can be radiused (as shown) to increase flow efficiency and performance. While the illustrated embodiment includes six flow (or swirl)passages 144, it will be appreciated that the number of passages can be varied. In addition, while theflow passages 144 all have a uniform offset from thelongitudinal passage 84, it should be appreciated that the passages can have no offsets, uniform offsets, varying offsets, and/or combinations thereof. - According to at least some embodiments, the
metering orifice 159 is formed by a passage that controls the flow rate between thedischarge passage 146 and the passage bounded by thevalve head 92 and thevalve seat 94. Moreover, in some embodiments, themetering orifice 159 is defined by anannular flow passage 160 at this location.FIGS. 11A and 11B illustrate anannular flow passage 160 according to some embodiments of the present technology. In these embodiments, theannular flow passage 160 is defined by an annular gap between anannular flange 162 on theplunger 70 and thewall 164 of thelongitudinal passage 84 in thevalve body 74. Theplunger 70 can include anannular groove 184 adjacent to thevalve head 92. Thegroove 184 can function to increase the volume downstream of theannular flow passage 160, thereby increasing the pressure drop across theflow passage 160 and increasing exit velocity. As noted above, the center section of the plunger includes abearing surface 155. It will be noted that it is desirable to have a tight clearance between this bearing surface and the wall of thepassage 84 to ensure centering of the plunger within thepassage 84. As can be seen inFIGS. 11A and 11B , a relatively larger clearance can be provided between theplunger 70 and the wall of thepassage 84 in the region defining theannular flow passage 160. -
FIGS. 11C and 11D , illustrate adischarge passage 146 andannular flow passage 160 according to certain other embodiments of the present technology. In these embodiments, thelongitudinal passage 84 in thevalve body 74 includes an increaseddiameter portion 168 in its proximal end, while theplunger 70 has a generally constant diameter, except for an increaseddiameter portion 170 at its proximal end adjacent to thevalve head 92. Although not shown, theplunger 70 can include an annular groove adjacent to thevalve head 92 to increase the volume downstream of theannular flow passage 160, thereby increasing the pressure drop across theflow passage 160 and increasing exit velocity. In these embodiments, thedischarge passage 146 is defined by the space between theconstant diameter portion 173 of theplunger 70 and the increaseddiameter portion 168 of thelongitudinal passage 84. It should be noted that theconstant diameter portion 173 of theplunger 70 can also function as abearing surface 155 in the manner described above. Likewise theannular flow passage 160 is defined by the annular gap between the increaseddiameter portion 170 of theplunger 72 and the increaseddiameter portion 168 of thelongitudinal passage 84. -
FIGS. 11E and 11F , illustrate adischarge passage 146 andannular flow passage 160 according to certain other embodiments of the present technology. In these embodiments, theplunger 70 can exhibit a generally constant diameter along its length except for thevalve head 92. Theplunger 70 can include anannular groove 184 adjacent to thevalve head 92 to increase the exit velocity in the manner discussed above. Thelongitudinal passage 84 in thevalve body 74 can exhibit a generally constant diameter, except for an increased diameterinterior portion 180. Thedischarge passage 146 is defined by the annular space between theplunger 70 and the increased diameterinner portion 180 of thepassage 84. Theannular flow passage 160 is defined by the annular gap between theplunger 70 and theportion 182 of thelongitudinal passage 84 that is located proximal to (i.e., outwardly from) the increased diameterinterior portion 180. A portion of theplunger 70 can also function as abearing surface 155 in the manner described above in to ensure centering of the plunger within thepassage 84. Accordingly, it is desirable to have a tight clearance between this bearingsurface 155 and theportion 187 of thepassage 182 that interfaces with the bearing surface. Further, as can be seen inFIGS. 11E and 11F , a relatively larger clearance can be provided between theplunger 70 and the wall of thepassage 84 in theportion 182 of thepassage 84 defining theannular flow passage 160. - The
discharge passage 146 and metering orifice 159 (e.g., annular flow passage 160) can be sized and configured in accordance with the desired performance characteristics or desired applications and/or environments. For example, a relativelysmall discharge passage 146 can act as a flow restrictor on theorifice 159. In particular, if the cross-sectional area of the discharge passage is smaller than that of themetering orifice 160, e.g.,annular flow passage 160, thedischarge passage 146 will restrict the maximum flow rater through theorifice 159. Conversely, increasing the size of thedischarge passage 146 increases volume of fluid that is stored in the discharge passage when the injector 10 is closed. An increased volume of stored fluid can increase the momentum, e.g., by the fluid from the external fluid source, required to initiate injection. Accordingly, in some embodiments, thedischarge passage 146 can be sized and configured so that it does not restrict fluid flow through themetering orifice 159, while still providing adequate control over the start of injection. It may be desirable to provide a volume for thepassage 146 such that all of the volume ofpassage 146 is purged each cycle/operation of the device, to assure that no fluid remains inpassage 146 from one cycle to the next to reduce the potential for formation of deposits inpassage 146 associated with the high heat exposure of the fluid residing withinpassage 146. It may also be desirable to providepassage 146 with a small volume to reduce or minimize loss of angular momentum of the fluid between the swirl plate and theannular orifice 160. - A relatively high exit velocity from the
annular flow passage 160 is beneficial for better fuel atomization. Accordingly, in some embodiments, the injector 10 can be configured to maximize the velocity of fluid exiting theannular flow passage 160. The exit velocity from theannular flow passage 160 can be increased by increasing the pressure drop across theannular flow passage 160. In some embodiments, the exit velocity from theannular orifice 160 is increased by increasing the pressure drop across theannular flow passage 160. One way to increase this pressure drop is by increasing the pressure indischarge passage 146, which can be accomplished by reducing flow restrictions upstream of the discharge passage. Accordingly, in some embodiments, the pressure in thedischarge passage 146 is maximized by minimizing upstream flow restrictions. The pressure drop across theannular flow passage 160 can also be increased by reducing the length of the annular flow passage. However, while decreasing the length of theannular flow passage 160 tends to increase exit velocity, it can also make the injector more sensitive to manufacturing tolerances. Accordingly, in some embodiments, the length of theannular flow passage 160 is minimized, within the constraints of manufacturing tolerances, in order to increase exit velocity from the flow passage. - The cross-sectional area and length of the
annular flow passage 160, i.e., themetering orifice 159, can be empirically determined during design and manufacture in order to provide the desired injection characteristics, including, for example, injection flow rate and distribution. In this regard, increasing the annular cross-sectional area of theflow passage 160 will generally increase fluid flow fluid flow, but will also tend to decrease the velocity of fluid flow. Likewise, the length of theannular flow passage 160 can be empirically determined during design and manufacture in order to provide the desired injection characteristics. For example, in the embodiments ofFIGS. 11A and 11B , thelongitudinal passage 84 in thevalve body 74 has a constant diameter (at least in the region that defines the annular flow passage 160). Accordingly, the length of theannular flange 162 on theplunger 72 can set the length of theannular flow passage 160. In these embodiments, theannular flange 162 can be sized (e.g., its length can be set) such that the stroke (i.e., normal operating range) of the injector 10 can vary without causing any significant change in the performance, e.g., spray uniformity and distribution, of the injector. Accordingly, the cross-sectional area of theannular flow passage 160 is generally constant over the normal operating range of the injector. - This concept is further illustrated in
FIGS. 12A-12H , which illustrate the operation of an injector having anannular flow passage 160 constructed in accordance with the embodiments ofFIGS. 11A-B . The stroke length or lift, e.g., the distance the plunger moves proximally from its closed position, continually increase betweenFIGS. 12A and 12H . As the stroke length increases, theannular gap 200 between thevalve head 92 and thevalve seat 94 increases. If the stroke length is too short, thegap 200 can restrict fluid flow through the annular flow passage 160 (or orifice). (See, e.g.,FIG. 12A ). Accordingly, in some embodiments, the stroke is set so that when the injector is fully open the cross-sectional area of thegap 200 is larger than that of theannular flow passage 160. - The length of the
annular flow passage 160 can be decreased to increase the velocity of fluid flow through thepassage 160. As noted above, increase fluid velocity through thepassage 160 can provide increased atomization of the fluid that is discharged from the injector. In the embodiments represented byFIGS. 11A and 11B , for example, the length of theannular flow passage 160 can be controlled by the stroke of theplunger 70. In particular, this length decreases as stroke length increases. At some point, the length of theflow passage 160 can become too short to provide good flow control and characteristics from theannular flow passage 160. In particular, as this length of thepassage 160 decreases, the ability to maintain a constant cross sectional area for the annular flow passage can become more sensitive to manufacturing tolerances. As this occurs, the performance, e.g., flow rate, of the injector may begin to fluctuate with stroke length. Further, as the distal end of theannular flange 162 moves proximally past junction of thevalve seat 94 and thepassage 84, the cross-sectional area will continue to increase with increasing outward movement of the plunger. Accordingly, in some embodiments, the length of the annular flow passage is minimized, within manufacturing tolerances, while the cross-sectional area of the flow passage is held constant. - Accordingly, the stroke length and
annular flow passage 160 can be set, e.g., through empirical testing during design and manufacture, in order to provide the desired injector operating characteristics. Further, according to some embodiments, proportional control can be used to provide variable flow from the injector. For example, proportional control can be used to adjust the stroke length (i.e., plunger lift) and accordingly the length of theannular flow passage 160. - As shown in the drawings, the
annular flow passage 160 is located inwardly from thevalve seat 94. Accordingly, when the injector 10 is closed, theannular flow passage 160 is protected from exposure to the exhaust stream by the seal between thevalve head 92 and thevalve seat 94, thereby reducing, for example, soot accumulation and injector fouling. Injector fouling is further reduced because fluid flows out of theannular flow passage 160 whenever theplunger 70 is open. This constant outward fluid flow prevents contaminates from entering and/or flushes contaminants form the injector, thereby reducing injector fouling. -
FIG. 13 illustrates a water-cooledinjector 1010 according to at least one embodiment of the present technology. Theinjector 1010 includes many components that are the same or similar to those used in the injector 10 ofFIG. 1 . Unlike the injector 10 ofFIG. 1 , however, theinjector 1010 uses a cooling fluid, such as water, instead of the injectable fluid, e.g., diesel fuel, to cool the injector components. To that end, theinjector 1010 includes acooling flange 1300 mounted on the proximal end of the injector. As explained further below, thecooling flange 1300 circulates cooling fluid around the injector components that are adjacent or near the flow of exhaust gas in order to cool these components. - Like the injector 10 of
FIG. 1 , theinjector 1010 includes acoil subassembly 1012, a body subassembly 1014, anarmature subassembly 1016 and avalve subassembly 1020. Thecoil subassembly 1012, includes acoil 1022 wound on abobbin 1024 and acover 1025 for securing the coil in place on the bobbin. The body subassembly 1014 includes amain body 1028, atube 1030 and a fitting 1032. The proximal end of thetube 1030 is secured to the distal end of themain body 1028. In the illustrated embodiment, the proximal end of thetube 1030 is mounted over anannular protrusion 1035 that extends from the distal end of themain body 1028. The fitting 1032 mounts to the distal end of thetube 1030 opposite themain body 1028. In the illustrated embodiment, the fitting 1032 includes a reduceddiameter portion 1046 that is sized for insertion into the distal end of thetube 1030. Themain body 1028,tube 1030 and fitting 1032 can be made of stainless steel, for example, and can be secured together by suitable methods such as threaded connections, press-fitting, welding, brazing or crimping, among others. - The
armature subassembly 1016 includes anarmature 1050 and apin 1051. Thepin 1051 is mounted through a longitudinal passage inarmature 1050. Thepin 1051 may be secured to thearmature 1050 by welding, brazing, press-fitting or other suitable means, for example. Afirst portion 1052 of thepin 1051 extends proximally from thearmature 1050 and slidably engages with alongitudinal passage 1053 in the distal end of themain body 1028. A second portion 1054 of thepin 1051 extends distally in acounterbore 1055 formed in the distal portion of thearmature 1050 and slidably engages into alongitudinal bore 1059 in the proximal end of the fitting 1032. As discussed above, thearmature 50 in the injector 10 includes flow passages that are defined byflat portions 64 on the periphery of thearmature 50. Since theinjector 1010 does not include an internal cooling path for the injectable fluid, for example, diesel fuel, flow passages are not provided in thearmature 1050. Accordingly, thearmature 1050 may, for example, have a circular cross-section. - The
valve subassembly 1020 can have similar construction and operation as thevalve assembly 20 described above. In this regard, thevalve subassembly 1020 includes aplunger 1070, anadapter 1072, avalve body 1074, aspring 1076 and aspring retainer 1078. Theinjector 1010 includes aninlet port 1138 for supplying a fluid, e.g., diesel fuel, to the injector from an external source (not shown). The fluid flows through theinlet port 1138 and into amain chamber 1139 formed betweenmain body 1028 and thevalve subassembly 1020. Fluid from themain chamber 1139 flows through a plurality of flow passages (not shown) in thevalve body 1074 and into a discharge passage (not shown). The flow passages in thevalve body 1074 and the discharge passage can have the same general construction as theflow passages 144 anddischarge passage 146 that were described above in connection with the injector 10. In some embodiments, the flow passages can be axially offset, as described above, to create a swirling flow of fluid within the discharge passage 1146. - When the
coil 1022 is deenergized, theinjector 1010 is biased to its closed position by thespring 1076. Theinjector 1010 is moved to its open position by energizing thecoil 1022. When thecoil 1022 is energized, the flux path created by thecoil 1022 acts on thearmature 1050 to move the armature proximally (e.g., to the left inFIG. 13 ) within thetube 1030. As the armature moves proximally, thepin 1051 pushes against the plunger 1070 (and against the force of the spring 1076) to unseatvalve head 1092 fromvalve seat 1094. When thevalve head 1092 unseats from thevalve seat 1094, fluid flows from the discharge passage 1146, through an annular flow passage 1160, out through the gap between thevalve head 1092 and thevalve seat 1094, and into the exhaust stream. The annular flow passage 1160 can have the same general construction and operation as theannular flow passage 160 described above in connection with the injector 10. - When the
injector 1010 is connected to an exhaust component, components on the proximal end, including thevalve head 1092 andvalve seat 1094, will typically be exposed directly to the exhaust gases flowing through the exhaust component. As noted above, theinjector 1010 includes acooling flange 1300 that circulates cooling fluid around the injector components that are adjacent or near the flow of exhaust gas in order to cool these components. Thecooling flange 1300 includes alongitudinal passage 1310 configured to receive the proximal portion of themain body 1028. In the illustrated embodiment, themain body 1028 andlongitudinal passage 1310 includereciprocal threads 1312 for securing theinjector 1010 to thecooling flange 1300. Alternatively, themain body 1028 can be secured to thecooling flange 1300 by welding, brazing, crimping, press-fitting or other suitable means. Thecooling flange 1300 also includes anannular counterbore 1313 formed in its proximal face outwardly from and concentrically with thelongitudinal passage 1310. Anend cap 1314 is mounted on proximal end of thecooling flange 1300 to seal off thecounterbore 1313 and define acooling chamber 1316. Theend cap 1314 can be secured in place by suitable means such as brazing, crimping, welding, press-fitting or threaded connection. Theflange 1300 includes aninlet port 1320 andoutlet port 1322 that are fluidly connected to the cooling chamber throughlongitudinal flow passages 1323 formed in thecooling flange 1300. The inlet and outlet ports can be connected to an external source (not shown) for circulating cooling fluid through thecooling chamber 1316 in order to cool the proximal end of theinjector 1010. - As is shown in
FIG. 14 , theinjector 1010 can be mounted to anexhaust component 1330 for injecting a fluid, such as diesel fuel, into an exhaust stream flowing through apassage 1332 in the exhaust component. For this purpose, theinjector 1010 includes mounting features configured to mate with reciprocal mounting features on theexhaust component 1330. According to at least one embodiment, the mounting features include mountingapertures 1334 on theinjector 1010 that align withreciprocal apertures 1336 on the exhaust component. Fasteners, such asbolts 1338, extend through the apertures 1134 in theinjector 1010 and thread into the apertures 1136 in theexhaust component 1330 to secure the injector to the exhaust component.Spacers 1342 can be positioned on thefasteners 1338 before the fasteners are installed. Thespacers 1342 can help dissipate from the injector. Agasket 1340 can be interposed between theinjector 1010 and theexhaust component 1330 to seal against gas leaks. -
FIGS. 15A and 15B illustrate another water-cooledinjector 1010B according to at least one embodiment of the present technology. Theinjector 1010B includes many components that are the same or similar to those used in theinjector 1010 ofFIG. 13 . Accordingly, like reference numerals are used to identify like components and only the primary differences between theinjectors injector 1010B are integrally formed with one another. This composite structure is identified withreference number 1350 inFIG. 11B . - In addition, the
injector 1010B has a different path for fluid flow through the injector. In this regard, thefluid inlet 1138B is formed in the distal end of the fitting 1032B. Fluid from theinlet 1138B flows into alongitudinal passage 1354 in the fitting. Fluid then flows into thetube 1030 and through alongitudinal passage 1354 in thearmature 1050B. Apin 1052B extends from the proximal end of thearmature 1050 and engages against the distal end of theplunger 1070. Thepin 1052B includes alongitudinal passage 1354 that is in fluid communication with thelongitudinal passage 1354 of thearmature 1350.Outlets 1358 in the proximal end of the passage open into themain chamber 1039B. Fluid from the main chamber 1139B flows through a plurality of flow passages (not shown) in thevalve body 1074 and into a discharge passage (not shown). The flow passages in thevalve body 1074 and the discharge passage can have the same general construction as theflow passages 144 anddischarge passage 146 that were described above in connection with the injector 10. In some embodiments, the flow passages can be axially offset, as described above, to create a swirling flow of fluid within the discharge passage 1146. - The
injector 1010 is moved to its open position (seeFIG. 15B ) by energizing thecoil 1022. When thecoil 1022 is energized, the flux path created by thecoil 1022 acts on thearmature 1050 to move the armature proximally (e.g., to the left inFIG. 15B ) within thetube 1030. As the armature moves proximally, thepin 1050B pushes against the plunger 1070 (and against the force of the spring 1076) to unseatvalve head 1092 fromvalve seat 1094. When thevalve head 1092 unseats from thevalve seat 1094, fluid flows from the discharge passage, through an annular flow passage, out through the gap between thevalve head 1092 and thevalve seat 1094, and into the exhaust stream. The annular flow passage can have the same general construction and operation as theannular flow passage 160 described above in connection with the injector 10. -
FIG. 16 illustrates ahydraulic circuit 1600 that can be used to supply fluid to aninjector 1602 according to certain embodiments of the present technology. Thehydraulic circuit 1600 can include afluid supply 1604 that delivers pressurized fluid to the inlet of theinjector 1602 through acontrol manifold 1606. Thefluid supply 1602 can include atank 1610 and apump 1612. The inlet of thepump 1612 can be fluidly connected to thetank 1610 through afilter 1618. Thecontrol manifold 1606 can includecontrol valve 1614 that is moveable between open and closed positions. According to at least some embodiments the control valve can be a solenoid-operated valve. The inlet of thecontrol valve 1614 can be fluidly connected to thepump 1612 through thefilter 1618, while the outlet of the control valve can be connected to the inlet port of theinjector 1602. Thecontrol valve 1614 is normally biased closed for fail-safe conditions. During operation of thehydraulic circuit 1600, thecontrol valve 1614 can be maintained in its open position, e.g., by the solenoid, to allow pressurized fluid to be supplied from the pump to the injector. An electronic controller (not shown) can be used to selectively energize theinjector 1602 to inject fluid into an exhaust gas stream, for example. When theinjector 1602 includes a cooling flow path such as described in connection with the injector 10 ofFIG. 1 , thehydraulic circuit 1600 can include areturn flow line 1622 from theinjector 1602 and thetank 1610. Accordingly, when theinjector 1602 is closed, fluid can be pumped from thetank 1610 through theinjector 1602 and back to the tank through the return line to cool the injector in the manner described above. Thereturn flow line 1622 can include a pressure relief valve to maintain the pressure at theinjector 1602 above a minimum threshold pressure when thecontrol valve 1614 is closed. - The
control manifold 1606 can include apressure sensor 1620 for monitoring the fluid pressure between thecontrol valve 1614 and theinjector 1602. According to some embodiments, thepressure sensor 1620 can be used to control dosing from the fluid injector. For example, look-up table can be developed to correlate inlet pressure to dosing rates, e.g., fluid flow rates, from the injector. Based on the pressure reading from the sensor, an electronic control unit can determine the flow rate from the injector and can in turn be used to control the operation of the fluid injector. - The pressure sensor can also be used for on board diagnostics, including, for example, detecting leaks in the hydraulic circuit and failure of the control valve. For example, when the control valve is commanded to be open, an absence of pressure can indicate failure of the control valve. A fluid leak can be detected by activating the
pump 1612, and thereafter closing thecontrol valve 1614 while monitoring the pressure sensor detected by the pressure sensor. A decreasing pressure reading under these conditions can indicate a fluid leak between thecontrol valve 1614 and theinjector 1602. - While this disclosure has been described as having exemplary embodiments, this application is intended to cover any variations, uses, or adaptations using the general principles set forth herein. It is envisioned that those skilled in the art may devise various modifications and equivalents without departing from the spirit and scope of the disclosure as recited in the following claims. Further, this application is intended to cover such departures from the present disclosure as come within the known or customary practice within the art to which it pertains. While this disclosure has been described as having exemplary embodiments, this application is intended to cover any variations, uses, or adaptations using the general principles set forth herein. It is envisioned that those skilled in the art may devise various modifications and equivalents without departing from the spirit and scope of the disclosure as recited in the following claims. Further, this application is intended to cover such departures from the present disclosure as come within the known or customary practice within the art to which it pertains.
Claims (5)
1. An injector for controllably injecting a fluid into an exhaust stream, the injector comprising:
a housing defining a chamber for storing the fluid;
an orifice comprising an annular flow passage in fluid communication with the chamber; and
a valve member for controlling the flow of fluid from the chamber, through the orifice and into the exhaust stream.
2. The injector of claim 1 , wherein the annular flow chamber is interposed between the chamber and the valve member.
3. The injector of claim 2 , wherein the valve member comprises a valve head and valve seat formed in an outer surface of the injector that faces the exhaust stream and a valve head, the valve head being movable between closed position at which the valve head engages the valve seat and blocks fluid flow through annular orifice the and an open position at which the valve head is spaced away from the valve seat in the direction of the exhaust stream to permit fluid flow through the annular flow passage.
4. The injector of claim 3 , wherein valve member seals the orifice from exhaust gas flow when the valve member is in its closed position.
5. The injector of claim 3 , wherein the valve member further comprises a plunger for moving the valve head between its open and closed positions.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/621,838 US20140054396A1 (en) | 2012-08-21 | 2012-09-17 | Fluid injector |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US201261691495P | 2012-08-21 | 2012-08-21 | |
US13/621,838 US20140054396A1 (en) | 2012-08-21 | 2012-09-17 | Fluid injector |
Publications (1)
Publication Number | Publication Date |
---|---|
US20140054396A1 true US20140054396A1 (en) | 2014-02-27 |
Family
ID=50147131
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/621,838 Abandoned US20140054396A1 (en) | 2012-08-21 | 2012-09-17 | Fluid injector |
Country Status (1)
Country | Link |
---|---|
US (1) | US20140054396A1 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2559174A (en) * | 2017-01-30 | 2018-08-01 | Delphi Int Operations Luxembourg Sarl | Control valve assembly and method of manufacturing thereof |
US20180328249A1 (en) * | 2018-07-25 | 2018-11-15 | Tenneco Automotive Operating Company Inc. | Reagent injector |
WO2019113307A1 (en) * | 2017-12-06 | 2019-06-13 | Continental Automotive Systems, Inc. | Outward opening injector for exhaust aftertreatment systems |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6279842B1 (en) * | 2000-02-29 | 2001-08-28 | Rodi Power Systems, Inc. | Magnetostrictively actuated fuel injector |
US6712296B1 (en) * | 1999-10-01 | 2004-03-30 | Robert Bosch Gmbh | Fuel injection valve for internal combustion engines |
US20070210189A1 (en) * | 2004-05-14 | 2007-09-13 | Willibald Schurz | Nozzle Assembly And Injection Valve |
US20080236147A1 (en) * | 2007-03-30 | 2008-10-02 | Continental Automotive Systems Us, Inc. | Reductant delivery unit for selective catalytic reduction |
-
2012
- 2012-09-17 US US13/621,838 patent/US20140054396A1/en not_active Abandoned
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6712296B1 (en) * | 1999-10-01 | 2004-03-30 | Robert Bosch Gmbh | Fuel injection valve for internal combustion engines |
US6279842B1 (en) * | 2000-02-29 | 2001-08-28 | Rodi Power Systems, Inc. | Magnetostrictively actuated fuel injector |
US20070210189A1 (en) * | 2004-05-14 | 2007-09-13 | Willibald Schurz | Nozzle Assembly And Injection Valve |
US20080236147A1 (en) * | 2007-03-30 | 2008-10-02 | Continental Automotive Systems Us, Inc. | Reductant delivery unit for selective catalytic reduction |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2559174A (en) * | 2017-01-30 | 2018-08-01 | Delphi Int Operations Luxembourg Sarl | Control valve assembly and method of manufacturing thereof |
GB2559174B (en) * | 2017-01-30 | 2020-04-08 | Delphi Tech Ip Ltd | Control valve assembly and method of manufacturing thereof |
US11506164B2 (en) | 2017-01-30 | 2022-11-22 | Delphi Technologies Ip Limited | Control valve assembly and method of manufacturing thereof |
WO2019113307A1 (en) * | 2017-12-06 | 2019-06-13 | Continental Automotive Systems, Inc. | Outward opening injector for exhaust aftertreatment systems |
US20180328249A1 (en) * | 2018-07-25 | 2018-11-15 | Tenneco Automotive Operating Company Inc. | Reagent injector |
US10683786B2 (en) * | 2018-07-25 | 2020-06-16 | Tenneco Automotive Operating Company Inc. | Reagent injector |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
CA2655129C (en) | Method and apparatus for reducing emissions in diesel engines | |
US8973895B2 (en) | Electromagnetically controlled injector having flux bridge and flux break | |
US10465582B2 (en) | Reagent injector | |
US9759113B2 (en) | Coaxial flow injector | |
US9683472B2 (en) | Electromagnetically controlled injector having flux bridge and flux break | |
EP2279335B1 (en) | System for purging a device | |
US20080302089A1 (en) | Dispensing System with Remotely Mounted Metering Device | |
US20140054396A1 (en) | Fluid injector | |
US11174773B2 (en) | Reagent injector | |
CN107060954B (en) | Injection system for purifying exhaust carbon smoke particles and control method | |
US20190170037A1 (en) | Diesel dosing unit having an anti-coking injector assembly, and methods of constructing and utilizing same | |
US10704444B2 (en) | Injector fluid filter with upper and lower lip seal | |
US20190170104A1 (en) | Anti-coking injector assembly for a diesel dosing unit, and methods of constructing and utilizing same |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: INTERNATIONAL ENGINE INTELLECTUAL PROPERTY COMPANY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:SCULL, NICHOLAS JEREMY;REEL/FRAME:031380/0865 Effective date: 20121207 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |