JPS58500293A - engine fuel injection system - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] engine fuel injection system 1. Field of invention The present invention relates to a fuel injection system for an internal combustion engine, and in particular to a pressurized fuel injection system. includes a fuel pump that periodically transmits energy from the fuel pump to the fuel injector through a conduit. The present invention relates to a fuel injection system.

2. Explanation of the leading nucleus' Many types of fuel injection systems supply pressurized fuel from a fuel pump. A cam-driven system that periodically transmits through a conduit to seven or more fuel injectors. Includes fuel pumps. Typically, these fuel injectors are spring-biased to the closed position. and opens when the pressure at the fuel injector exceeds a predetermined pressure level. fuel injection When the magnitude of the pressure/force at the injection valve decreases below a predetermined limit level, The force given by spring deflection is applied when the needle valve of the fuel injection valve is fully opened, and the 7th ring of the ennon is Terminate fuel injection into the engine.

British Patent Specification Application No. 4#3, /2'1, dated /93/2003, is of the type mentioned above. Invention by Amery relating to improvements in fuel injection systems is disclosed. In the system disclosed by Amery, the fuel injector is.

The valve opens when the fuel pressure at the valve reaches a predetermined level. Fuel injection valve υ1 To force the fuel injector to close at a predetermined time, independent of the fuel pressure at the exit end. In order to generate fluid pressure to be applied to the fuel injection well/back 1 side, an auxiliary cover is installed. A system operated control valve is provided.

According to Amery's system, the initiation of fuel injection is initiated by a mechanically driven fuel point. pump timing, while the termination of fuel injection is based on a cam-actuated control valve. depends on the pressure applied to the closed piston/in the fuel injector.

The unique feature of fuel injection/stem driven at engine speeds is that low engine speeds Due to the slower f7f action of the fuel pump in the is rapidly declining.

U.S. Patent No. discloses a fuel injection system that utilizes a pressure accumulator to maintain a uniform fuel supply pressure; ing. A spring-biased servo valve in the fuel injector controls the opening and closing of the fuel injector. 1, U.S. time No. ≠, 03 Otsu, /9.2 (Nakayama), each fuel injection - Eliminates fuel dripping from fuel injection nozzles following Zels' exit Contemplated associated fuel injection/stem systems are disclosed.

U.S. Pat. No. 3,93; 2,7 (Imberley et al.) is Disclosed is a fuel injection nozzle with control. Uniform fuel pressure at the fuel injection valve In this common rail/stem, which utilizes an accumulator to provide the power source.

The opening of the nozzle valve is controlled by a compression spring in a conventional manner; Independent means are provided for controlling the excursion force of the nozzle valve between (U.S. Pat. Third. J/Otsu, SO Otsu No. (Steiger) has uniform pressure in the fuel injection valve. In addition to regular rail fuel injection/stem systems that utilize pressure accumulators to maintain power levels. Discloses the type of

Detailed description of the invention The present invention provides a method for periodically transmitting a pressurized P lux of fuel through a conduit. Intended for fuel injection/stem of internal combustion engines, including fuel pumps, electronic circuit means and fuel The fuel injection valve includes fuel injection valve means. Electronic circuit means are coupled to the pump/ Generates electrical output signals to measure performance and control mechanical/non-performance. fuel injection The valve means is coupled to the electronic circuit means and for generating an electrical output signal between an open position and a closed position. The fuel injection valve is connected to the conduit through which the mechanical displacement between the fuel injection valve and the a predetermined variable time interval independent of the arrival of the end of the pressurization pulse of fuel delivered to the stage; Then, the pressurized fuel of the measured value is injected into the work/no/no/su/da. It has become.

An important aspect of this/stem is that it is transmitted through a conduit to a remotely located fuel injector. The timing of fuel injection is the installation of a fuel injection system that generates high-pressure fuel. and duration are independent of the arrival time or duration of the pressure/emission pulse at the fuel injector. In relation to this, the inside of the fuel injector is closed.

One other important aspect of the present/stem is that the inlet of the fuel injector, prior to the start of fuel injection, This is caused by the reflection of numerous fuel pressure waves through the fuel line extending between the The fuel pressure level at the fuel injector is determined by summing the pressures the fuel in order to be able to reach at least a predetermined minimum value in engine RPM. Independently controllable time and interval opening/closing after the arrival of fuel pressure/loss to the fuel injection valve It is its ability to remain in a fixed position.

Drawing description The invention is particularly pointed out in the claims.

However, other objects and advantages of the present invention, together with its operation, will be apparent when combined with the accompanying drawings. A better understanding can be obtained by referring to the detailed explanation given below. can.

FIG. 7 provides an overview of the various elements of the r/l) embodiment of the present fuel injection/stem. This is a schematic diagram.

FIG. 2 is a sectional view of a fuel injection valve according to the present invention.

FIG. 3 is a block diagram of various elements of the invention.

Figure q is a partial cross section of a fuel injection pump used in combination with the stem of the present invention. It is a diagram.

Figure 5 shows the relative timing between opening and closing of the fuel injection valve and the fuel injection pump. This is a tie diagram.

FIG. 4 is a block diagram of another embodiment of the invention.

Description of preferred embodiments In order to better demonstrate the advantages of the present invention and its contribution to the technical field, preferred The hardware implementation will now be described in detail. , FIG. It is shown. The low pressure fuel supply pump 7'IO supplies fuel from the fuel tank 12. and passes fuel through a fuel filter 14 to a pair of fuel distributor blocks 16 and 18. Communicate. The high pressure in-line fuel injection pump 20 is connected to the fuel distributor block 16. Accepts the fuel supply from 18 and routes the fuel high pressure hull to blocks 16 and 18. Retransmit at regular intervals. Bon f20 is mouth-gut-bot/yu (Robert Bosch), American Bosch (Amer 1can Bosch) , or of the type commercially produced by C-A, (2). these commercial Generally available pumps have control ranks and control mechanisms for pump output control and pump delivery. The vent valve is not necessary and must be modified. I horn 20 is Enno The camshaft should also be coupled to a camshaft driven at For a fall! 7 per cam to produce the pumping stroke! one equal Includes ``Cam S-Near'' (cam 1 obes).Fuel pressure/Grus is , occurs intermittently at time intervals due to the pumping stroke of the pump 20 The pump 20 transmits the fuel pressure to the distributor blocks 16 and 18 at the speed of sound. reached, where the fuel pressure/loss is divided into ≠ parts and ≠ one for each distributor block. to separate fuel injectors. After the fuel pressure/ξ Lus arrives at the fuel injector At independently timed intervals, the fuel injector is energized by electronic circuit means (not shown). is automatically activated to direct a predetermined amount of fuel from the fuel injector to a selected/starting point in the engine. It is designed to be metered into the combustion chamber of the da.

In FIGS. 2 and 3, the electronic circuit means 22 is configured to control the temperature, the revolutions per minute of the Ennon ( RPM), manifold pressure, turbocharger exhaust pressure, throttle position, and engine seven or more parameters representative of the emission levels of the various constituent elements of the exhaust gas. An engine performance sensor for sensing various engine operating parameters. Contains a stage.

The electronic circuit means 22 also provides a It also accepts a control signal representative of the desired level. (not shown) electronic control hand The stage receives the control signal and the output of the encoder performance sensor means.

Generates an electrical output signal that modulates the operation of the remaining elements of the fuel injector/stem of the present invention. The performance of the engine can be adjusted by changing the timing and duration of the fuel injector output. In one other F position/stem of the electronic circuit means 22, which is adapted to control the be.

The feedbank and control elements of the electronic circuit means 22 and the electronic sensor means are It is well known to those skilled in the art and is therefore not disclosed in particular detail.

Pressurized pumps of fuel periodically generated by a fuel insulator driven by an The fuel is transmitted through conduit 24 to fuel injection valve 26 . Fuel pressure bus A is below 4 into the conventional nozzle section creating increased pressure within the nozzle cavity 32. It is flushed through passage 28. In this first or open position, the servo valve 36 is , pressurized fuel flows from passage 34 through hole 38 and outlet passage 40 into spring chamber 42. make it possible to go to Spring chamber 42 is in fluid communication with upper nozzle cavity 44. and is therefore also in fluid communication with the first valve face 46 of the knee valve or valve means 48. . A second valve face 50 is positioned within the lower nozzle cavity 32 .

When the servo valve 36 is in the first or open position as shown in FIG. The first valve front 46 and the first! The valve face 50 is subject to equal fluid pressure, but the second As a result of the large surface area of the first valve face 46 compared to the surface area of the valve face 50, The downward spring biasing force is applied to the first valve face 44 by the biasing means or biasing spring 52. As a result of being applied to the valve seat 54, the valve means 48 remains in firm contact with the valve seat 54. and pressurized fuel flows from the lower nozzle cavity 32 through the metering orifice 56. be prevented from passing into the /ring of the ring.

When the valve actuation means 58 is actuated by an electrical output signal coming from the electronic circuit means 22 Then, the +j-bo valve 36 is displaced downwardly by the shaft 60 of the actuating means 58. valve Actuation means 58 are commercially available items of a type well known to those skilled in the art.

Team Co of Sus E1 Monote, California V-70 servo valve voice coil dryer manufactured by The bar assembly functions satisfactorily.

When the servo valve 36 is displaced downwardly to the second position by the shaft 60 of the valve actuation means 58 and the larger diameter upper end section of the servo valve 36 is closer to the lower cutoff point of the valve ridge 62. extends slightly downwardly so that pressurized fuel flows from passage 34 through hole 38 and into passage 40. end one. In this second position, above the larger diameter of the servo valve 36 The lower portion of the area is displaced to a position approximately indicated by reference numeral 64 and communicates with hole 38. The communication of the road 40 is not obstructed. In the second position, the lower area of the servo valve 36 is larger. The area above the threshold diameter 0 is displaced to a point below the upper part of the ridge 66, and the area above the spring chamber 42 is The pressurized fuel passes through the passage 40, the hole 38, the valve ridge 66, and the fuel discharge passage 68. and allow it to flow.

The fuel discharge pipe 1 is connected to the discharge lower o, and the discharged fuel is returned to the fuel tank. It is possible to

While the fuel pressure is still in the fuel injector 26.

Electronic circuit means 22 energizes the valve actuation means to reposition servo valve 36 to the second position. I'll try it. Therefore, the high pressure fuel is still within the lower nozzle cavity 32, but through the passage 4o. through the seventh face 46 of the valve means 48. Valve means by pressurized fuel Number 48! The pressure exerted on the front face 50 is due to the downward pressure exerted by the spring 52. overcoming the deflection force and displacing the valve means 48 in an upward direction which opens the valve means 48 and pressurizes it. The fuel flows through the fuel metering orifice 56 into the engine ring. and make it possible.

After a predetermined time interval determined by the circuit means 22, it is demagnetized and the servo is activated. The valve 36 is allowed to be returned to the first or open position by the bias spring 71.

The high pressure fuel is then retransmitted through outlet 40 into spring chamber 42 and valve means 48 is displaced downward to close valve 48 and terminate the flow of fuel from lower nozzle cavity 32. make it complete. In this way, the pressure within the lower nozzle cavity 32 is equal to or lower than when injection is initiated. The injection of fuel ends while the current remains substantially unchanged. During the entire fuel injection time , maintaining a high substantially uniform pressure differential across the fuel metering orifice 56 is , a cylinder that maximizes engine performance with a favorable flow rate of fuel and good atomization. gives rise to a fuel distribution of type O).

In some applications, the rate at which the valve means 48 is displaced may be reduced to reduce the rate at which the valve means 48 is displaced per hour. It may be desirable to more gradually increase the amount of fuel injected into. child The effect of this is to adjust the displacement of the shaft 60 of the valve actuating means 58 to adjust the rate of displacement of the servo valve 36. control or in and above the spring chamber 42 when the servo valve 36 is displaced to the second position. Inside the nozzle gap 4/1 (=-5 layers), the fuel outlet 6 is opened so that the pressure gradually decreases. This is easily achieved by dimensioning 8.

The solenoid valve actuating means 50 may be used in other ways to affect the combustion process and the performance of the engine. It can be adjusted with.

In the figure, a suitable type for use in conjunction with the present invention is shown. 7) Plants A partial cross-sectional view of the to/su/da is shown at the beginning of its po/f 0 working stroke, and the resection On the right hand side of the part is at the end of its pumping stroke. The pose is Includes fuel openings 72 and 74 on diametrically opposite sides of the cylinder/cylinder.

When the valve 77 and the valve 76 are in the lower position shown on the left valve side in the figure, the fuel opening Portions 72 and 74 are partially exposed, allowing fuel from the low pressure fuel supply bomb 7'IO to Fuel is supplied from fuel distributor blocks 16 and 18 through fuel outlet 80 and fuel chamber 78. Allowing flow out of mouths 72 and 74. The - or turn of this fuel flow is , to clean the pumping chamber 78 and during the preceding downward stroke of the silane gloss 76. Remove any air bubbles and steam that may have formed.

When driven by a cam (not shown), the scilla/gloss 76 begins its upward movement. This upward movement causes the valve ridge 82 to close off the fuel openings 72 and 74. Department closure). At this point, the fuel in the pumping chamber 78.

The fuel begins to be pressurized and is discharged through the fuel outlet 80, and begins to generate fuel pressure and e-lux. This fuel pressure pulse is then transmitted to the fuel distributor block through the fuel outlet 8C1:/. to one of locks 16 and 18. After a given upward displacement.

The lower ridge 84 of the piston/76 rides over the lower edge of the fuel openings 72 and 74 (opening opening), establishing fluid communication between the fuel openings 72 and 74 and the transverse hole 86. . Thus, the drain path is opened and fuel can flow from the pressurized pumping chamber 78 into the passageway. 88 and lateral hole 86, and the fuel openings 72 and 7 as shown on the right hand side of Fig. 41M and can be discharged.

The initial establishment of fluid communication between the fuel openings 72, 74 and the lateral holes 86 requires an effective pump. Finish the pressing stroke, but the sillage/gloss will not be the same as it is shown on the right-hand side of the figure. Its upward movement is slowed down until it stops at its uppermost position as Continue with - During the next downward stroke of the planter 76, fuel is pumped from the fuel outlet 80. During the initial portion of the downward stroke, fuel flows into the fuel opening 72 and into the fuel opening 72. 74 and also flows into the pumping chamber 78 via a transverse hole 86 and a passage 88. Blanc At the end of the downward displacement of Kutahu 60, the ridge 82 extends beyond the top of the openings 72 and 74. ' to allow fluid communication between the fuel opening and the pumping chamber 78 as described above. shall be. During the entire downward stroke of the sill/gloss 76, the pumping chamber 78 is filled. so that the fuel openings 72 and 74 are fully exposed at the end of the stroke.

Enables reduction of total silane gloss lift displacement required for correct pumping action That's necessary.

Limiting the discharge of fuel from the highly pressurized fuel line into the Bonf working chamber 780 In order to do this, a pressure responsive valve is provided at the fuel outlet 80 of the fuel pump to reduce the It may be desirable to maintain a predetermined minimum pressure of water at both times.

This pressure water seepage is slightly smaller than the pressure of the fuel supplied by the fuel supply pump It would be small.

This type of pressure relief valve is well known to those skilled in the art and is It is commercially available from companies such as Bert Bosch.

Figure 1 and Figure ≠: A, K:, '+3'J-'C Fuel injection pump 2 In connection with the operation of 0, the supply of low pressure fuel is connected to the fuel distributor blocks It is circulated through outlet 80 into pumping chamber 78 of fuel pump 20 . present invention In another embodiment, the fuel drain/tube designated by reference numeral 21 in FIG. ``By combining the supply of fuel under low pressure, the can be done.

In this embodiment, a one-way check valve connects each individual fuel injector to the exhaust lower 0. and each fuel injector has an additional passage ( (not shown). This arrangement allows the fuel pressure/gurus to be the high pressure input to the fuel injector. allows low pressure fuel to flow into passage 28 through the check valve whenever the shall be. Through the check valve, flow of S low 1 - + "', t' +: From discharge lower 0 It can also be coupled to the lower nozzle cavity 32 through an extending passageway. This arrangement is Ambient temperature fuel flow is circulated through valve means 48 in a manner well known to those skilled in the art. Allows the needle valve to be cooled. Formation of air bubbles and cavities within the system In order to prevent the fuel pressure from contaminating, the fuel pressure should be reduced more gradually. The lower part of the binuton 70 near the crest 84 can be attached with a conical 1-lap or straight The diameter can be made smaller. Alternatively, to achieve the same result, A smaller diameter orifice ζ can be provided within the channel 88.

In FIG. Time-related line diagrams are drawn/drawn. The opening closure line 90 is connected to the pressure at the injector 26. It represents the arrival of forces p and tf. Each pressure gas has fuel openings 72 and 74 This occurs when the ridge portion 82 of the runger 76 closes the gap. The X-axis 91 represents one closure of the opening in the pump. The vertical distance between the × axis 91 and the opening closing line 90 The direct distance corresponds to the travel time of fuel pressure and fuel from the bomb f to the injector. Open Mouth opening line 92 represents the arrival of the end of the pressure liquid at injector 26 . this What is the end? 7: -1', T, A≦]・(C). Lines 94 and 96 are the clamp Measuring a given amount of fuel at a given time, which can vary with respect to shaft angle and engine RPM. The electronic circuit means 32 of the present invention is used to open and close the valve means 48 as shown in FIG. A possible fuel injection timing table for wet/dry conditions is shown.

The length of the line indicated by reference numeral 98 is the length of the line indicated by reference numeral 98. at jooRPM between the occurrence of the leading edge of the Corresponds to 1 hour interval. This large time between the closing of the opening and the opening of the valve means 48 Interval (・, ~, 7 fuel pressure zerus is driven by Ennon fuel 7f! 77° through the conduit to the fuel injector 26 multiple times. engineering / ]/ The high pressure fuel/P lux between the fuel pump driven by / and the fuel injection valve 26 is The standing wave caused by the reflection of the number is 1. The fuel pressure at the inlet of the natural injection valve 26 is The sum of the amplitudes of the various standing waves can be substantially enlarged as a result.

Therefore, at low speeds, the effective fuel pressure at the fuel injector 26 is It can be many times the fuel pressure generated by the driven fuel pump. Therefore, Maintaining uniform, high fuel pressure at the fuel injectors 26 over the entire speed range As a result, a uniform amount of fuel can be generated per unit time for all engine operating conditions. The flow rate and uniform spray pattern of the material can be maintained. maximum available Engine torque is controlled by electronically preprogramming the shape and limits of line 96. can be restricted. This is the injection into the cylinder at a particular engine speed. limits the maximum amount of fuel injected, thereby limiting the maximum torque available .

the opening closure line, as represented by the line designated by the reference numeral 100; 90 and the opening of the valve means 48 is such that the higher speed engine RPMVc It is shorter. The reason is that the fuel pump driven by the engine produces In order for the generated fuel to reach the injection valve 26, it must be at a low speed engine RPM. Because it requires a larger crank angle in short work/non-RPM than in It's a good thing. Therefore, is it an effective fuel? The effect of the standing wave that multiplies the pressure is that it Most widely used in slow ennon RPMs where it is most needed due to the low amplitude of the pressure waves. This is necessary due to the high amplitude of the pressure waves generated by the pump. does not decrease with increasing RPM.

In FIG. 4, another embodiment of the fuel injector/stem of the present invention is disclosed.

This particular embodiment shown works with a ≠7 ring diesel ennon. It works. A single valve means 28 is coupled to each of the cylinders of the ennon. ing. A single valve actuation means 48 and serve valve 36 are provided for the entire system. and is located far from the valve stages 48. The fuel selector valve 102 , coupled between the inlet passage 28 of the valve means 48 and the conduit 24, while the fuel selector Valve 04 is coupled in series with outlet passage 40. Selector valves 102 and 104 is driven by a shaft synchronized with the rotational position of the engine. The selector valve The flow of fuel arriving at these inlet sides is subsequently routed to the two/s/das of the Ennon. Direct mechanically. What if the firing order of a particular ennon is /,! , 3, if t For example, at that time, the selector valves 102 and 104 switch the pressurized fuel cell nozzle to the exhaust gas. will selectively direct the cylinders in that order. Selector valves 102 and 1 04 are coupled to simultaneously direct fuel pressure/cerno to the same valve means 48. It is.

Low pressure fuel source 0 is coupled to direct fuel under pressure to selector valve 102. and fuel distributor blocks 16 and 18 in a manner similar to that described in connection with fuel distributor blocks 16 and 18. to the system. The remaining elements of the system depicted in Figure 4 include other features. There is essentially no difference from what was mentioned above in connection with this. The main advantage of the system shown in figure is that The mechanical-ware costs of the stem are substantially reduced. Sele The valves 102 and 104 are relatively inexpensive and require only a single valve actuation means 40 and a single service. - 3 liters is required for the entire cono/stem.

The engine fuel injection stem disclosed herein can be modified in a number of ways. and may take many embodiments other than the preferred form specifically described above. will be clear to those skilled in the art. For example, the valve actuation means 58 may To control the operation of the injection valve 26, it may be electrically controlled, but hydraulically or pneumatically. Can operate with air pressure.

The electronic circuit means 22 of the present invention comprises an ennon or a mass elastic system which is an element of an ennon. Disable fuel injection from selected 7s/das to affect the oscillatory torsional behavior of the stem. It can be specifically programmed to be withheld partially or completely. all engines When the cylinder output load is the same, the cylinders other than the selected one are operated with a higher load. Fuel from selected cylinders for a period of time to enable operation Injection can be withheld. Equalize temperature and other ennon parameters Therefore, fuel injection can be withheld alternately from different cylinders.

We therefore expressly wish to protect all such modifications which fall within the true spirit and scope of the invention. - It is intended by the claims to:

Ward 1 Figure 5 Figure 2 Figure 3 Figure 6 international search report

Claims (1)

[Claims] 1. Fuel for periodically transmitting pressurized fuel through conduit 24; In a fuel injection/stem for an internal combustion engine that includes a fuel pump 20, the system is coupled to an ennon for: (a) measuring ennon performance and for generating an electrical output signal to control ennon performance; and (b) a fuel coupled to said electronic circuit means 22 and coupled to said conduit 24 for converting an electrical output signal into a mechanical displacement between an open position and a closed position. An injector means 26 for receiving pressurized pulses of fuel transmitted through a conduit to the fuel injector means. an internal combustion engine comprising: fuel injector means 26 adapted to inject a measured amount of pressurized fuel into the seven rings of said engine at predetermined variable time intervals, independent of arrival or termination; Fuel injection system for engines. 2 a second fuel injection valve hand coupled to said electronic circuit means 22 and coupled to said conduit 24 for converting an electrical output signal ° into a mechanical displacement between an open position and a closed position; the second fuel injector means of the engine at predetermined variable time intervals, independent of the arrival or termination of the pressurized flow of fuel communicated through the conduit to the second fuel injector means; Claim 3, further comprising second fuel injector means 26 adapted to inject a measured amount of pressurized fuel into the cylinder. The electronic circuit means selectively opens either the fuel injector means 26 or the second fuel injector means 26 when the electronic circuit means is independently controllable in the presence of fuel pressure. according to claim 2, characterized in that a measured amount of pressurized fuel is selectively injected into the nozzle/drill or into the second nolling when: system. 4. A fuel injection system for an internal combustion engine comprising a fuel engine f20 for periodically transmitting pressurized fuel through a conduit, said system c: (a) for measuring engine performance; and electronic circuit means 22 coupled to the ennon for generating an electrical output signal to control ennon performance; fb) electronic circuit means 22 for converting the electrical output signal into a mechanical displacement between a first position and a second position; , valve actuation means 58 coupled to said electronic circuit means 22; (c) for transmitting pressurized fuel through the outlet passageway 40 when in the first position; valve actuating means 58 for receiving pressurized fuel through the outlet passageway and for receiving pressurized fuel through the conduit 24; servo valve 36 coupled to f20; and (d) a first valve face 46 coupled to the outlet passage 4o of the servo valve 36, and directing the valve means 48 to open! a second valve face 50 coupled through 24 to the fuel pump f20, wherein pressurized fuel is admitted by the fuel pump 20 to the second face 50 of the valve means 48. I'd like to say a word with you. and being adapted to inject pressurized fuel into said pump/injector when discharged from said first face 46 of said valve means 48 by said outlet passage 40 of said valve 36; include. Fuel injection system for internal combustion engines. 5. The electronic circuit means 22 includes engine performance sensor means coupled to the engine for sensing various performance parameters of the engine. /stem described in. 6. The electronic circuit means is coupled to the electrical performance sensor means for generating an electrical output signal in response to various electrical performance meter and control signals. 6./Stem according to claim 5, characterized in that it includes child control means. 7. The valve actuation means 58 has a shaft 60 displaceable between a first position and a second position. The /stem according to claim 1, characterized in that the stem comprises an electric lunoid 58. 8. Stem according to claim 1, characterized in that the valve means is biased to a closed position. 9. The amount of fuel f into the /s/da is determined by the arrival of fuel pressure and gas at said valve means or / according to claim g, characterized in that the step is carried out independently of the termination. When the surge valve 36 is displaced to the first position, the pressurized fuel is applied to the first face 46 of the valve means 48 to close said valve means 48; /Stem according to claim 9, characterized in that: 11. The /step according to claim 70, characterized in that when the servo valve 36 is displaced to the second position, pressure is relieved from the first face 46 of the valve means 48. Mu. 12. The /stem of claim 5, wherein the servo valve 36 is biased to a first position. 13. The system of claim 72, wherein the servo valve 36 is biased to the first position by a spring 71. 14. The stem according to claim g, characterized in that said valve means 48 is biased into a closed position by biasing means coupled to a first face 46 of said valve means 48. 15. The stem of claim 1, wherein the deflection means 52 includes a spring 52. 16. wherein the servo valve 36 includes a fuel discharge passage 68 for discharging fuel communicated from the first face 46 of the valve means 48 through the outlet passage 40 of the servo valve 36. /stem according to range 5. 17. The stem of claim 1, wherein the valve actuation means 58 is electrically controlled and hydraulically actuated. 18. The system according to claim 1, wherein the valve actuation means 58 is electrically controlled and pneumatically actuated. 19. The system of claim 5, wherein the valve actuation means 58 is electrically controlled and electrically actuated. 20 The engine performance sensing means measures revolutions per minute (RPM) of the engine. 7. The 7-stem according to claim 5, characterized in that: 21 The claim is characterized in that the engine performance sensing means measures a throttle position. /stem according to claim 20. 22 The engine performance sensing means measures manifold pressure. /Stem according to claim 20. 23. The /stem according to claim 20, wherein the engine performance sensing means measures the temperature of the engine. 24. The system according to claim 1B, wherein the cross-sectional area of the fuel discharge passage 68 controls the rate at which the valve means 48 opens. 25. The system of claim 1, wherein the cross-sectional area of the outlet passageway 40 of the servo valve 36 influences the rate of opening and closing of the valve means 48. 26. The system of claim 1, wherein the pressurized pulses of fuel are generated by mechanical pumping means. 27. The system according to claim 2B, characterized in that the pumping means includes a cam-operated silane polisher 76. 28, said pumping means includes a camshaft, said camshaft; 28. The system of claim 27, comprising a plurality of cams with equal cam ropes. 29. The system according to claim 1N, 2g, wherein the engine includes a crankshaft, and the camshaft of the pumping means is rotationally driven in a periodic relationship with the crankshaft of the engine. . 30. The stem according to claim 27, characterized in that the camshaft of the pumping means is rotated at a revolutions per minute that is half the revolutions per minute of the crankshaft of the engine. . 31. A system according to claim 29, characterized in that the camshaft of the pumping means rotates at the same speed as the ennon crankshaft. 32. The system according to claim 29, characterized in that the camshaft of the pumping means comprises a pump. 33. The system according to claim 29, characterized in that the camshaft of the pumping means rotates at a revolutions per minute twice the revolutions per minute of the crankshaft of the ennon. stem 34; the pumping means includes a pumping chamber 78 having a fuel opening 72; 78. The system according to Section 2g. 35. The cylinder head 76 entranoses a predetermined volume of fuel into the pumping chamber 78 by closing off the fuel opening 72 during an initial portion of its pumping stroke. Systems described in Scope Section 3j Mu. 36. The system of claim 3, wherein the fluid reservoir of the mechanical pumping means includes a restriction orifice. 37. The system of claim 311, wherein the outlet of the fluid reservoir includes an overflow valve. :38 Said Cyranotsuya 76 is in front during the second part of its pumping stroke. The fuel opening 72 is opened to connect the insulating chamber 78 and the fluid storage chamber, and 34. The system of claim 33, further comprising removing pressure from the pumping chamber 78. 39. The system of claim 1, wherein the pumping chamber 78 is connected to the conduit 24. 40. The pumping chamber 78 is coupled to the conduit 24 by a pressure responsive valve that maintains a minimal pressure differential between the conduit 24 and the pumping chamber 78. A system according to paragraph 341. 41 Directly connected to the conduit 24 at a point between the fuel pump 20 and the servo valve 36 5. The system of claim 4, comprising fuel distributor blocks coupled in columns. 42, wherein the fuel distributor block includes a one-way check valve having an input coupled to a low pressure fuel supply, and wherein pressure within the fuel distributor block is at the input side of the check valve. the fuel distributor block is adapted to allow fuel to flow from the low pressure fuel source into the fuel distributor block when the pressure is less than the pressure applied to the fuel distributor block. The system according to paragraph 47. 43, the opening time of said valve means 48 is controlled by said electronic circuit means 22, and the opening time of said valve means 48 is controlled by said electronic circuit means 22; The amount of fuel injected into the cylinder is now limited as a function of engine speed. 7. The system according to claim 6, characterized in that: 44, the initial opening of said valve means 48 is at a speed commensurate with the timing requirements of the engine. 7. A system according to claim 6, characterized in that the system is controlled by said electronic circuit means as a function of power and load. 45. Closing of said valve means 48 is preprogrammed according to a predetermined torque curve stored in said electronic circuit means, said torque curve being one of various engine performance parameters. 7. The system of claim 6, wherein the system is modifiable in response to a meter. 46, further comprising a plurality of valve means 48, each of said valve means 48 being coupled to inject fuel into a separate cylinder of said engine. The system according to claim 1. 47(a) synchronized with the rotational position of the engine for selectively directing fuel pressure from the fuel pump 20 through the conduit 24 to a second valve face 50 of selected ones of the valve means 48; a first selector valve means 102 which is synchronized with the rotational position of said ennon and which selector valve means 102 of said valve means 48; In order to establish fluid communication between the first valve face 46 and the servo valve 36 of the 3. The system of claim 1, further comprising second selector valve means 104 coupled to the outlet passageway 40 of the servo valve 36 for the purpose of controlling the servo valve. 418 The first selector valve means 102 and the second selector valve means 104 include rotary valves that are rotationally driven in synchronization with the rotation of the tool/horn. 48. The system of claim 47, characterized in that: 49. The system of claim 1I♂, wherein the rotary valve is mechanically driven by a rotating member of the engine. 50, a fuel tank for periodically transmitting a pressurized stream of fuel through conduit 24; In a fuel injection system for an internal combustion engine including a fuel pump F20, the system comprises: fa) an ennon coupled to the ennon for sensing various performance parameters of the engine and generating an ennon performance signal; performance sensing means; (b) for receiving engine performance signals and control signals and for emitting electrical output signals; (c) electronic circuit means 22 coupled to said encoder performance sensing means for generating a signal; (d) coupled to said fuel pump 20 through conduit 24; and a servo valve 36 displaceable by the valve actuating means 58 between a first position and a second position, the servo valve 36 transmitting pressurized fuel through the outlet passage 40 when in the first position; is adapted to receive pressurized fuel through the outlet passageway 40 when the engine is in the position. servo valve 36; and (e) a first/valve front face 46 coupled to the outlet passage 40 of the front twelve third valve 36; a second valve face 50 coupled to said fuel bong 7''20 through a tube 24; 50 and discharged from the first face of the valve means 48 by the outlet passage 40 of the servo valve 36. Injecting a measured amount of pressurized fuel into the ennon/ring. The valve means 48 is adapted to terminate injection of pressurized fuel into the cylinder 7 when the v-+t' valve 36 is displaced to the second position. Thereby, at predetermined variable time intervals, a measured amount of pressurized fuel is delivered to said valve means 48, regardless of the arrival or termination of the pressurized fuel supply to said valve means 48. Fuel injection/spring for internal combustion engines, including injection into the 7th ring of the engine. Tem. 51 wherein said engine includes a plurality of seven rings and said electronic circuit means 22 includes an electrical output for withholding injection of fuel from a selected compression stroke of a selected cylinder; 51. The system of claim 50, further comprising generating a force signal. (b) delivering pressurized pulses of fuel through conduit 22 to fuel injection valve 26; transmits f russ (c) Comparing the actual engine operating parameters to the desired engine operating parameters; (d) opening the fuel injector 26 at a predetermined time after the fuel pressure pulse arrives at the fuel injector 26 and increasing the fuel pressure to the fuel injector 26; Arrival or termination of pulse is irrelevant Relatedly, in response to the injector control signal, the fuel injector 26 is closed after a predetermined injection time. A method for injecting a measured amount of fuel into/a ring of an internal combustion engine at predetermined variable time intervals comprising the steps of; 53, the time interval between the first arrival of each fuel pressure at the fuel injection valve 26 and the opening of the fuel injection valve 26 is such that the time interval between the output side of the fuel injection pump 20 and the input side of the fuel injection valve 26 is The fuel input pressure at the fuel injector 26 can be substantially increased as a result of the sum of the pressures caused by the standing waves reflected between the 53. The method of claim 52. 54. The method of claim 53, including the step of: utilizing the pressure of the fuel to open and close the fuel injector 26. 55. Claim 53 includes the step of electrically comparing the desired engine operating parameters and actual engine operating parameters to generate an injector control signal. Method described. 56. The fuel injection valve 26 is biased to a closed position.Claim 511. Methods listed at the top. 57, the injector control signal is controlled by mechanically varying the servo valve 36 between the first and second positions. The method according to claim j6, characterized in that the method includes the step of converting into Law. 58, selectively coupling a first face 46 of the fuel injector 26 to the conduit 24 and coupling a second face 50 of the fuel injector 26 directly to the conduit 24, between the first and second positions; sa The imbalance of forces that selectively open and close the fuel injector 26 in response to mechanical displacement of the first front face 46 of the fuel injector 26 and the second! 58. The method of claim 57, comprising: causing the front face 50 to intersect with the front face 50. 59. Mechanical change of servo valve between first and second positions using fuel pressure 5g. The method of claim 5g, comprising increasing the force generated by the position to open and close the fuel injector 26.