Abstract:
Fuel injectors and methods of fuel injection allowing direct control of the flow of fuel at an intensified pressure to the needle. A valve, typically a spool valve, is placed in the fuel passage between the intensifier actuation piston and the needle, and controlled by a control valve which may be independent of the control valve controlling the coupling of actuation fluid and a vent to the intensifier actuation piston. This allows achievement of intensification before initiating injection, and control of multiple injections in a single injection event while maintaining fuel intensification throughout the duration of the injection event. Various embodiments are disclosed, including embodiments having multiple intensifiers, having control of pressure over the needle, having two stage control valve systems for control of intensifier actuation fluid, and combining control of one of the intensifiers and the valve controlling flow of intensified fuel to the needle for injection.

Description:
CROSS-REFERENCE TO RELATED APPLICATION  
       [0001]    This application claims the benefit of U.S. Provisional Patent Application No. 60/475,022 filed May 30, 2003 and U.S. Provisional Patent Application No. 60/485,948 filed Jul. 7, 2003. 
     
    
     
       BACKGROUND OF THE INVENTION  
         [0002]    1. Field of the Invention  
           [0003]    The present invention relates to the field of fuel injectors, and more particularly to intensifier type fuel injectors.  
           [0004]    2. Prior Art  
           [0005]    Intensifier type fuel injectors are well known in the prior art. As an example, see U.S. Pat. No. 5,460,329. That patent discloses an electromagnetically actuated spool valve for controlling the coupling of an area over an intensifier piston to an actuating fluid under pressure or to a vent, the intensifier piston driving a smaller piston to intensify the pressure of fuel for injection purposes. While various types of valves are known for use with such injectors, the valves generally control the flow of actuation fluid to and from the area over intensifier piston.  
           [0006]    While control valves of the foregoing type can be made relatively small and fast-acting, control of actuation fluid in this manner for direct fuel injection has certain limitations. In particular, a diesel fuel injector may intensify fuel pressure to a pressure on the order of 20,000 psi or higher, at which pressures the fuel will undergo substantial compression. This, in turn, means that there must be substantial actuation fluid flow into the chamber over the larger piston of the intensifier. In that regard, while, by way of an example, in an intensifier having an area ratio of 9:1, the pressure of the actuating fluid over the larger piston will only be {fraction (1/9)} of the intensified pressure, the flow of actuation fluid required to achieve the compression and intensification of the fuel will be nine times that required because of the compression of the intensified fuel, thereby resulting in at least as much volumetric compression in the actuation fluid over the intensifier piston as in the intensified fuel. Consequently, intensification on actuation of the control valve(s) requires significant actuation fluid flow, and is therefore less than immediate. Also, this flow requirement sets the minimum size for the electrically operated control valves, and further requires de-intensification between injection events, making multiple injections during a single injection event difficult and energy consuming.  
       
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS  
       [0007]    [0007]FIG. 1 is a perspective view of one embodiment of fuel injector in accordance with the present invention.  
         [0008]    [0008]FIG. 2 is a cross-section of the injector of FIG. 1.  
         [0009]    [0009]FIG. 3 is a cross-section of the upper injector body assembly of FIG. 2, taken on a larger scale.  
         [0010]    [0010]FIG. 4 is a cross-section of the lower injector body assembly of FIG. 2, taken on a larger scale.  
         [0011]    [0011]FIG. 5 a  is a cross section of an exemplary control module  26  as used in the fuel injector embodiment of FIG. 1.  
         [0012]    [0012]FIG. 5 b  is a diagram is a control fluid flow diagram for the control module of FIG. 5 a.    
         [0013]    [0013]FIG. 6 is a block diagram for an injector assembly wherein the intensifier is powered by the fuel rail pressure through a three-way intensifier control valve.  
         [0014]    [0014]FIG. 7 is a block diagram for an injector assembly wherein the intensifier is powered by engine oil under pressure rather than fuel.  
         [0015]    [0015]FIG. 8 is a cross section of a lower injector assembly in accordance with another embodiment of the present invention.  
         [0016]    [0016]FIG. 9 is a cross section of an injector in accordance with the present invention having multiple intensifier pistons.  
         [0017]    [0017]FIG. 10 a  through  10   c  show top, front, and side views of a combustion cell or air-fuel module incorporating the present invention.  
         [0018]    [0018]FIG. 11 shows a section view of the combustion cell through section line  1 - 1  of FIG. 10 a.    
         [0019]    [0019]FIG. 12 shows a section view of the combustion cell through section line  2 - 2  of FIG. 10 a.    
     
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS  
       [0020]    [0020]FIG. 1 is a perspective view of one embodiment of fuel injector in accordance with the present invention. The major parts of the fuel injector visible in this figure are the injection tip or nozzle, generally indicated by the numeral  20 , a lower injector body assembly body  22 , and upper injector body assembly  24 , and a control module  26 .  
         [0021]    [0021]FIG. 2 presents a cross-section of the injector of FIG. 1 illustrating the cooperation of the injection tip  20 , the various parts of the lower injection body assembly  22  and the upper injector body assembly  24 . FIGS. 3 and 4 show the same cross-sections of the upper injector body assembly and the lower injector body assembly, respectively, on a larger scale. As illustrated in FIG. 3, the upper injector body assembly  24  is comprised of an intensifier piston  26  operative to provide a high or intensified pressure to the fuel in the intensifier chamber  28  in response to a downward force on the intensifier piston. The intensifier piston  26  may be driven downward by applying an actuating fluid pressure in region  30 , pressurizing the region above piston  32 , by applying actuating fluid pressure in region  34  above piston  36  operative against intensifier drive pin  38 , or by applying actuating fluid pressure to both regions  30  and  34 . In a preferred embodiment, the cross-sectional area of piston  32  is approximately three times the cross-sectional area of intensifier piston  26 , with piston  36  having a cross-sectional area approximately equal to six times the cross-sectional area of intensifier piston  26 . Thus, intensification ratios of approximately three, six and nine (by pressurizing the region over both pistons  32  and  36 ) may be achieved. These numbers, of course, are exemplary only and any ratios may be used as desired. Alternatively, a control may be used to pressurize either one or the other but not both regions  30  and  34  at the same time, or by way of further alternative, the aspects of the invention inherent in the lower injector body assembly and control may be practiced with simply a single intensifier actuation piston if desired.  
         [0022]    Certain details of the upper injector body assembly  24  are not illustrated in FIG. 3, though the same are obvious design aspects that would be apparent to anyone of reasonable skill in the art. These, of course, include the porting for applying actuation fluid pressure to region  30  and/or to region  34 , for venting the regions below intensifier actuation pistons  32  and  36  to avoid the possibility of a hydraulic lock, and the means to return the intensifier piston  26  and the actuation pistons to their upper position and replenish the fuel in the intensifier chamber  28  between injection cycles, whether by fuel supply pressure in the intensifier chamber, a return spring, a combination of fuel pressure and return spring, or something else.  
         [0023]    Now referring to FIGS. 2 and 4, cross-sections of the lower injector body assembly  24  may be seen. The injection tip  20  is of a generally conventional design, the check valve or needle  40  therein being encouraged downward to a check valve closed position by coil spring  42  operative against spring endplates  44  and  46 . The upper spring endplate  44  is also in contact with the lower end of the spool  48  of a spool valve operative within a spool valve body  50 . This spool valve either couples region  52  providing fuel under an intensified pressure to the internal region of injector tip  20  from port  54  coupled to the intensifier chamber  28  (see also FIG. 3), or couples region  52  through port  56  to a lower pressure vent or drain region. In the position shown, the spool valve member  48  is positioned within the spool valve body  50  to couple region  52  to the drain  56  so the fuel in the check valve region is not substantially pressurized, and to block flow from port  54  to region  52 .  
         [0024]    Not readily visible in the cross-section of FIG. 4 is a porting of fluid typically under the same pressure as the intensifier actuation fluid pressure to the region  58  above the spool  48 . As shall be subsequently described in detail, an actuation fluid under pressure is controllably applied to the region  58  above spool  48  to control the position of the spool. In particular, at the beginning of an injection cycle, in the embodiment being described, intensifier actuation fluid under pressure will be applied to region  30  over the actuator piston  32  (see FIG. 3), to region  34  over the intensifier actuation piston  36 , or both regions  30  and  34 , resulting in intensified fuel pressure in intensifier chamber  28  and, thus, port  54  (FIG. 4). Shortly thereafter, typically after the intensification pressure has been obtained, actuation fluid under pressure is applied to region  58  to move spool  48  to a downward position against spring  42 , coupling the intensified fuel in port  54  through port  52  to initiate injection through the check valve  40  which, as a result of high pressure fuel, will move upward against coil spring  42  to initiate fuel injection.  
         [0025]    Injection is terminated by first venting region  56  above spool  48 , allowing coil spring  42  to move the spool to the position shown to terminate the supply of intensified fuel to the check valve, followed by the controlled venting of the intensifier actuation piston or pistons to allow the return of the intensifier piston(s) to its starting position and the refilling of the intensifier chamber with fuel under the effect of fuel supply pressure or the combination of fuel supply pressure and return spring (not shown). It should be noted that while in the preferred embodiment, the actuation fluid for the intensifier and for spool  56  is fuel, other actuation fluids such as engine oil may be used as desired.  
         [0026]    Now referring to FIG. 5 a , a cross section of an exemplary control module  26  (see FIG. 1) may be seen. The major porting for the module includes an actuation fluid supply port S that supplies fluid under the actuation pressure to three solenoid actuated pilot spool valves and two main spool valves to be described. The porting also includes a vent port V, also communicating with the three solenoid actuated spool valves and the two main valves, and further includes three outlet passages  62 ,  64  and  66  coupled to the injector body assemblies hereinbefore described. Two of the solenoid actuated spool valves or pilot valves, indicated by the numerals  68  and  70 , indirectly control the coupling of ports  62  and  64 , respectively, to the source S or vent V ports. The ports at  62  control the coupling of fluid to region  34  over upper intensifier piston  36  (see FIG. 3), with port  64  controlling the coupling of fluid to region  30  over lower intensifier piston  32 . Port  66  controls the coupling of actuation fluid to region  30  over intensifier actuation piston  32 . Since the spool valve  68  and  70  (FIG. 5 a ) may be identical, details of only one will be described.  
         [0027]    In particular, spool valve  68  is comprised of a solenoid coil  1  controllably magnetizing a magnetic circuit which includes spool  72  of the spool valve and magnetic members  86  and valve body  88 , the spool  72  being encouraged to the right-hand position by the spring washer  90  at the right-hand end of the spool and magnetically attractable to a left-hand position as desired. While the spool valve  68  in FIG. 5 may be a magnetically latching spool valve, magnetic latching is not a necessity, as a non-magnetic latching spool valve may also be used if desired. Similarly, other return springs, dual coil actuators, etc. may be used as desired, as the specific valves described are exemplary only and not a limitation of the invention.  
         [0028]    Pilot valve  68  controls a main valve, generally indicated by the numeral  72 , while spool valve  70  controls main valve  74 . The main valves  72  and  74  may be substantially identical, both being spool valves in the embodiment shown. With respect to main valve  72 , the right end of the spool  76  therein contains a small bore with sliding piston pin  78  therein which is pressurized on the left end by the pressure of the fluid in the supply port S and is vented at the right end. At the left end of spool  76  is another piston pin  80  within a corresponding larger bore in the spool  76 , with the right end of pin  80  being coupled either to the supply port pressure or the vent pressure as controlled by the position of spool  72  in pilot valve  68 . Thus, the spool valve  68  controls the position of spool  76 , allowing a small spool valve with a very short stroke to cause a longer stroke in a somewhat larger diameter spool valve to control a relatively large flow area by a relatively small pilot spool valve. In that regard, for clarity, actual proportions are not shown. The position of spool  76  in turn controls the coupling of port  62  to the intensifier actuation fluid supply or the vent, port  62  being coupled to region  34  above intensifier piston  36 . Similarly, pilot valve  70  controls main valve  74  and, thus, the coupling of port  64  coupled to region  30  over intensifier piston  32  to the intensifier actuation fluid pressure or vent in a similar manner.  
         [0029]    Finally, a third spool valve, generally indicated by the numeral  82 , controls the position of spool  84  which in turn controls the coupling of port  66  to the actuation fluid supply or vent, depending on the position of the spool. Port  66  is coupled to the region  58  (FIG. 4) over spool  48  to control the coupling of fuel under the intensified pressure to the check valve. This valve, when in the unactuated position, should preferably couple the check valve fluid to vent, not to the supply pressure, as a failsafe feature, and for the same reason, preferably this valve particularly is not magnetically latching, the return spring overcoming the inherent magnetic force caused by the residual magnetism in the magnetic circuit, including the spool.  
         [0030]    The advantage of the assembly hereinbefore described is that the speed with which actual injection may be initiated and terminated is extremely high, as it is controlled by a small spool valve  82  controlling a small fuel injection fluid flow after the intensified pressure is reached, as opposed to the flow of intensifier actuation fluid which is many times higher. Thus, while the two-stage control for the application of intensifier actuating fluid to the intensifier piston or pistons may be substantially slower, that does not affect the speed of initiation or termination of injection. In that regard, for a single combustion event, the present invention is fast enough to use multiple injections of small quantities of fuel for pilot-injection purposes and/or for extending the overall injection period for such purposes as engine operation under low load and/or lower engine speed operation using a single intensification cycle, and in fact, the intensified pressure of the fuel may be changed during the multiple injections by control of pilot valve  68  and  70  during or between those injections. Thus, pilot injection may be at one fuel pressure, and the subsequent injection or injections at a different pressure, typically but not necessarily a higher pressure. In a preferred embodiment, the control module of FIG. 5 a  measures approximately 1 inch wide by 2 inches high by ½ inch thick.  
         [0031]    [0031]FIG. 5 b  provides a simplified diagram of the control module of FIG. 5 a . As may be seen therein, in this exemplary embodiment, the supply and vent ports are coupled to all five valves. The upper pilot valve, which in this embodiment is a 3-way spool valve, controls the upper main 3-way main spool valve controlling the large intensifier  36 , the next pilot valve, which in this embodiment is also a 3-way spool valve, controls the upper main 3-way main spool valve controlling the small intensifier  32 , with the bottom valve, which may be the same as the pilot valves, controls the injection flow control valve. Preferably the injection flow control valve is not magnetically latching as a fail safe feature, though the pilot valves may be non latching also to remove intensified pressure from the actual intensified fuel flow control spool valve spool  48 .  
         [0032]    Other embodiments disclosed herein add control of fluid pressure over the needle  40  by including an additional valve mechanically coupled, in many embodiments actually integral with, the spool  48 . This provides substantially simultaneous shifting between a) pressure over the “top” of the needle and “vent” pressure at the lower end of the needle, and b) vent pressure over the top of the needle and fuel at an intensified pressure for injection at the bottom of the needle.  
         [0033]    Before going into the detailed operation of the injector, block diagrams of embodiments of such overall injector assemblies may be seen in FIGS. 6 and 7. FIG. 6 provides a block diagram for an injector assembly wherein the intensifier is powered by the fuel rail pressure through a three-way intensifier control valve. Similarly, a three-way injection control valve is used to control the coupling of rail pressure or a vent to the hydraulically controlled needle control valve in the lower assembly of the injector. Either or both of these control valves may be in other forms as desired, such as by way of example, either or both of the valves, as in the earlier embodiments, may be a pair of two-way valves, preferably solenoid operated spool valves using one or two actuator coils, with or without magnetic latching. The control valves may be single actuator spring return or double actuator, either of which may or may not include magnetic latching, though other variations of valves, including other variations of spool valves, may be used as desired.  
         [0034]    The embodiment of FIG. 7 is similar to that of FIG. 6, though the intensifier in this embodiment is powered by engine oil under pressure rather than fuel. If desired, the valve in the lower assembly of the injector could also be powered by engine oil under pressure, though this is not preferred. In any event, in the description to follow, as well as in the prior embodiments, either actuating fluid will simply be referred to as actuating fluid, whether by way of example, the actuating fluid is fuel rail pressure or engine oil rail pressure. The vent pressure may be atmospheric pressure or some other pressure, frequently a pressure somewhat above atmospheric pressure.  
         [0035]    Now referring to FIG. 8, a cross section of a lower injector assembly in accordance with one such embodiment of the present invention may be seen. This embodiment includes within the lower injector assembly, generally indicated by the numeral  100 , a spool  102 , a needle  104 , coil spring  106  with end caps  108  and  110 , and pins  112  and  114 . Also visible in FIG. 8 is intensifier piston  116 , which may be powered by fuel at rail pressure or engine oil under pressure, as controlled by electronically controlled valving as previously described and as is now well known in the art. With no pressure in the injector (neither rail pressure nor intensified fuel pressure), coil spring  106  pushes down on end cap  110 , pushing pin  112  against the top of needle  104  to hold the needle closed. At the same time, the coil spring  106  pushes upward on end cap  108  against pin  114 , which in turn pushes spool  102  upward to its maximum upward position. In that regard, in the specific embodiment, end  118  of spool  102  is larger than the diameter of the rest of the spool, and acts as a poppet valve to seal against valve seat  120  in the body of the injector, the poppet valve hereafter being referred to as poppet valve ( 118 , 120 ).  
         [0036]    In operation, the position of spool  102  is controlled by controllably coupling passage  122 , and thus chamber  124  over the top of spool  102 , to either rail pressure or a vent pressure. This is provided by a three-way needle control pilot valve, preferably a spool valve, shown schematically in the Figure, that may be of any of various types well known in the art. With passage  122  coupled to vent, the spool will be in its upper position because of spring  106  pushing upward on spring retainer  108  and in turn, on pin  114  pushing against the lower end of the spool. (The chamber in which the spring resides is vented.) In this position, fuel from the intensifier in passage  126 , whether at an intensified pressure or approximately rail pressure during the intensifier return, is blocked by the poppet valve ( 118 , 120 ) from flowing through passage  128  to the lower needle chamber  130 . At the same time, rail pressure is coupled from passage  132  through the spool valve and passages  134 ,  136  and  138  to chamber  140  over area  141  on the top of the needle  104  to hold the needle closed (down), the underside area  141  being vented.  
         [0037]    When the needle control pilot valve is in a position to couple rail pressure through passage  122  to chamber  124  over the spool  102 , the spool will move downward to its lower position, closing fluid communication between passage  132  and  134 , and coupling passage  134  to the vent  139 . It also closes communication between passages  144  and  128 , and opens the poppet valve ( 118 , 120 ), coupling intensifier chamber  142  to the lower needle chamber  130  through the passages  126  and  128 .  
         [0038]    Consequently, for an injection event, an intensifier control valve means, which can be a 3-way intensifier control spool valve, can be actuated to couple rail pressure to the intensifier to intensify the fuel pressure as in the previously described embodiments, followed by actuation of the needle control pilot valve to couple the intensified fuel to the lower needle chamber and venting the region over the needle to initiate injection. Injection may be terminated by movement of the needle control pilot valve and the intensifier control valve to the opposite states, preferably but not necessarily by first movement of the needle control pilot valve, followed substantially immediately by movement of the intensifier control valve, to the opposite states. This also opens fluid communication between passages  144  and  128 . Passage  144  is coupled to passage  146  having a valve at the top thereof coupled to a vent  147  and encouraged to the closed position by rail pressure on pin  148  acting on a seat at the top of passage  146 . This sets a lower pressure limit for the lower needle chamber  130 , in this embodiment, preferably to some fraction of the rail pressure.  
         [0039]    In the foregoing embodiment, if multiple injections are to be used, such as, by way of example, a pre-injection followed by one or more main injection, the intensifier control valve may be actuated to intensify the fuel pressure, with the needle control pilot valve being actuated multiple times during a single actuation of the intensifier control valve to provide the desired multiple injections without requiring the time and energy that would be associated with multiple pressure intensification cycles. Also, while the embodiment of FIG. 8 utilizes a poppet valve for coupling the intensified fuel to the lower needle chamber  130 , a spool valve on spool  102  may also be used for that purpose.  
         [0040]    In addition, the intensifier itself may have a single or a multiple, typically a dual, intensifier piston, that is, may be comprised of one or two driving pistons of equal or preferably unequal areas, preferably concentric or coaxial, each controlled by its own pilot control valve so is to be capable of achieving any of multiple intensified fuel pressures, such as described with respect to previously described embodiments and shown in FIG. 9. In the embodiment of FIG. 9, intensifying piston  202  might be given an area 3 times that of the intensifier piston  200 , with intensifying piston  204  having an area 6 times that of intensifier piston  200 , as before. Thus, intensification ratios of 3, 6 and 9 could be achieved by actuation of either or both control valves  206  and  208 .  
         [0041]    In the embodiment of FIG. 9, control valve  206 , schematically illustrated, also controls spool  210 , so that actuation of the intensifying piston  202  substantially simultaneously couples the intensified fuel through valve  210  through passage  220  to the lower needle chamber  212  to initiate injection. Injection is terminated by putting control valve  206  in the opposite state, blocking intensified fuel from the lower needle chamber  212  and coupling the lower needle chamber to a vent or relief valve through passage  214 . In this embodiment, pin  218 , subjected to rail pressure on the top thereof through porting, not all of which is not shown, provides a 2 to 1 relief ratio, so that the minimum pressure in the lower needle chamber  212  between injection events will be approximately twice rail pressure. The areas or area ratios may be set so that the residual pressure in the lower needle chamber  212  between injection events, together with coil spring  216 , will provide an upward force that is less than the downward force provided by rail pressure acting on the cross-sectional area of the spool when valve  206  is actuated.  
         [0042]    The advantage of the embodiment of FIG. 9 is that through the use of only two electronically controlled control valves, needle control and injection flow control are achievable, as are multiple intensification pressure ratios. The disadvantage, of course, is that needle control and flow control are integral with the lower intensification ratio control. This may be satisfactory in many applications, however, as for instance, one might provide pilot injection through the control of control valve  206  only, with control valve  208  being actuated after pilot injection but before main injection, so that substantial intensification is achieved before main injection is initiated. In other embodiments, a third control valve may be provided to decouple the needle control and injection flow control from the operation of either intensifier piston, thereby providing full flexibility in operation.  
         [0043]    In the disclosure herein, the word “actuation” and perhaps variations thereof have been used with reference to various control valves, normally electrically operated spool valves. It is to be noted that actuation is used in the general sense to indicate the change of the valve from one state to another state, whether by the application of electrical power, the removal or termination of electrical power or by some other or more complicated electrical sequence.  
         [0044]    [0044]FIG. 10 a ,  10   b  and  10   c  show a top, front, and side views of a combustion cell or air-fuel module similar to the device disclosed by U.S. Pat. Nos. 6,148,778 and 6,173,685. The combustion cell may include a fuel injector  91 , hydraulically actuated engine intake valves  92  and engine exhaust valves  94 , and the hydraulic control valves  96  and  98  to control the actuation of the engine valves. The disclosed fuel injector may be used in such a combustion cell, as the compact arrangement of the fuel injector control valves may allow the intake and exhaust valves to be positioned in close proximity to the fuel injector.  
         [0045]    [0045]FIG. 11 shows a section view of the combustion cell through section line  1 - 1  of FIG. 10 a . FIG. 12 shows a section view of the combustion cell through section line  2 - 2  of FIG. 10 a . The fuel injector and valves are shown relatively schematically, the Figures being presented to illustrate the suitability of the present invention to such applications.  
         [0046]    The above description discloses certain specific embodiments the present invention. It is to be understood by those skilled in the art that further variations and enhancements may be incorporated, depending on the application, without departing from the spirit and scope of the invention, including, but not limited to, the realization of the circuit in integrated circuit (IC) form. Thus while certain preferred embodiments of the present invention have been disclosed and described herein, it will be understood by those skilled in the art that various changes in form and detail may be made therein without departing from the spirit and scope of the invention. Similarly, the various aspects of the present invention may be advantageously practiced by incorporating all features or various sub-combinations of features as desired.