Improved apparatus for delivering fuel to an internal combustion engine

Abstract: A fuel injection system for an internal combustion engine has an improved apparatus for injecting fuel to each cylinder of the engine. The apparatus comprises a body having therein a fuel cavity (80) communicating with a port cavity (33), metering means (10) to selectively deliver fuel to the fuel cavity (80), and a port (32) in the body providing communication between the port cavity (33) and the exterior of the body. The port (32) has a valve means (34,35) including a valve element (34) adapted to co-operate with the port (32) to selectively open and close the port (32) and a valve stem (35) attached to the valve element (34), and a selectively operable electromagnetic means (40,41) within the body operably connected to the valve stem (35) to move the valve element (34) to open and close the port (32). The valve stem (35) extends from the port cavity (33) to the fuel cavity (80) through the electromagnetic means (40,41), and a passage (20) extends through the valve stem (35) communicating the port cavity (33) with the fuel cavity (80). Means are provided to supply gas to the fuel cavity (80) at least when the port (32) is open to convey fuel from the fuel cavity (80) through the valve stem passage (20) and the port cavity (33) to and through the open port (32).

Description: This invention relates to an apparatus such as a fuel injector for delivering fuel to an internal combustion engine; wherein metered quantities of fuel are delivered to each cylinder of the engine entrained in a gas, preferably a combustion supporting gas, such as air. The invention also relates to a fuel injection system for an internal combustion engine having such an apparatus or injector. It has previously been proposed to deliver a metered quantity of fuel to an engine entrained in a body of gas with the pressure of the gas being sufficient to effect delivery of the fuel via a valve controlled port, either directly into the cylinder of the engine, or into the induction system through which the air charge passes for delivery to the cylinder. This form of fuel metering and injection requires the supply of both fuel and gas to each metering and injecting unit associated with the respective cylinders of the engine. Such a fuel metering arrangement is described in WO87/00583. A number of operational factors must be considered in the design of the metering and injecting unit, including such factors as the weight of the valve controlling the delivery of fuel, including the valve stem, as inertia loadings and valve bounce are important in the maintenance of accurate fuelling. Also, the extent of the surfaces wetted by the fuel after it has been metered influences the variations in fuel quantity delivered to the engine on a cycle to cycle basis, and the response of the engine to changes in the metered quantity of fuel. In the metering system of WO87/00583, the valve stem an annular delivery fuel passage is provided around the valve stem between a fuel supply chamber and the valve, and hence this passage has a substantial surface area. Furthermore, the solenoid which actuates the valve is located on the side of the supply chamber remote from the valve, and the valve stem is very long. It is therefore desirable to provide a fuel injection system having an improved apparatus for injecting fuel to an internal combustion engine that is small and compact and will operate with the required reliability, accuracy and durability demanded with modern engines. There is therefore proposed an apparatus for injecting fuel to an internal combustion engine, comprising: a body having therein a fuel cavity communicating with a port cavity, metering means to selectively deliver fuel to the fuel cavity, a port in the body providing communication between the port cavity and the exterior of the body, valve means including a valve element adapted to co-operate with the port to selectively open and close the port and a valve stem attached to the valve element, selectively operable electromagnetic means within the body operably connected to the valve stem to move the valve element to open and close the port, and means to supply gas to the fuel cavity at least when the port is open to convey fuel from the fuel cavity to and through the open port, characterised by the valve stem extending from the port cavity to the fuel cavity through the electromagnetic means, and a passage extending through the valve stem communicating the port cavity with the fuel cavity, whereby the fuel from the fuel cavity is delivered entrained in said gas through the valve stem passage and the port cavity to and through the open port. Conveniently, the electromagnetic means is in the form of a solenoid having a coil disposed concentric to the valve stem with a co-axial armature attached to the valve stem. Preferably, the armature extends into, or is located substantially within, an annular space between the coil and the valve stem. The valve stem is preferably of tubular form with the valve element secured to one end and the other end open to receive the fuel. At the valve element end, communication is provided between the interior of the tubular valve stem and the port cavity. Preferably, the communication is arranged so a significant quantity of fuel may not be trapped in the tubular valve stem below the point of communication with the port cavity and so not pass into the port cavity. Conveniently, the fuel may be injected through the port directly into a combustion chamber of the engine. In the above proposed construction, a number of benefits arise in the operation of a fuel injection system having such fuel injecting apparatus. The passing of the fuel through a passage in the valve stem, such as is provided by the tubular valve stem, reduces the surface area to which the fuel is exposed as it passes from the point of metering to the port through which it is delivered to the engine, particularly in comparison with prior constructions where the fuel has passed through an annular passage. The surface area wetted by the fuel influences the delay that may occur between the variation of the fuelling rate at the point of metering and the consequent variation at the port where the fuel is delivered to the engine. During each injection cycle, and with changes in fuelling rates, there is a change in the thickness of the film of fuel adhering to the surfaces over which the fuel passes from the metering point to the delivery port. Accordingly, if the surface area in contact with the fuel is reduced, there is a reduction in the total quantity of fuel involved in changes in thickness of the fuel film. This is reflected in an improvement in the response time of the engine and a reduction in instability of the engine arising from variability in the quantity of fuel delivered between each cycle of the engine. There is also a benefit arising from locating the electromagnetic means, such as the solenoid assembly, between the fuel delivery port and the fuel metering point, as compared with previously proposed constructions wherein the fuel metering point is between the solenoid and the fuel delivery port. The resulting reduction in the length of the valve stem reduces the weight thereof, and reduces the natural frequency of the valve stem, and hence reduces the amount of valve bounce that may occur on valve closure. The relatively large quantities of fuel passing through the valve stem when the engine is operating at high loads provides a significant cooling effect on the solenoid at a time when the rate of heat generation is high. Also, location of the solenoid assembly between the fuel delivery port to the engine and the fuel metering point, and the symmetric external shape of the solenoid, enables that portion, or part thereof, of the fuel injecting apparatus to be recessed into the head of the engine to which the apparatus is fitted, thereby providing a reduction in overall height of the engine and fuel injecting apparatus assembly. This location also provides the ability for the fuel to be raised in temperature by heat input from the cylinder head, particularly at low fueling rates, and will assist in atomisation. A major use for the apparatus above described for injecting fuel to an internal combustion engine is in direct injection of fuel into individual cylinders of a multi-cylinder engine such as widely used in vehicles. Because of manufacturing cost considerations, it is customary to provide a single pump which provides the fuel from a fuel reservoir to each of the fuel injecting devices, with appropriate return lines to the fuel reservoir from each injecting device. Also, it is customary for cost saving reasons to provide a single pressure regulator to control the pressure differential between the gas and the fuel as supplied to each fuel injecting device. This construction results in a multitude of fuel lines between the fuel injecting devices and the fuel pump and pressure regulator, which significantly contribute to manufacturing costs. It will be appreciated that in this construction, the fuel and gas lines must be provided with suitable end connectors, which are usually threaded in order to provide an effective leak proof connection, and the provision of complementary threaded components on the fuel injecting devices, fuel pump and pressure regulator. The manufacture and assembly of these multiplicity of threaded components is a further cost factor. Also, additional costs are involved in the installing of the numerous fuel and gas lines. Further, the multitude of fuel and gas lines detract from the overall neatness of the installation. The use of the number of lines for the fuel and gas also present operational disadvantages as the resilient nature of the plastic lines usually used results in variations in line cross-sectional area with internal pressure, and so it is difficult to maintain the required control of the pressure differential between the fuel and gas supplies. In many engine applications, such as automobiles and outboard marine engines, the physical size of an engine and its associated accessories is of major importance. There is limited scope for reduction in the size of the engine itself, and accordingly it is important to maintain to a minimum the extent that accessories, added to the basic engine, increase the overall size thereof. In the light of the above discussed construction, operational and cost disadvantages of currently known fuel injection systems, it is also desirable to provide an improved fuel injection system, whereby these disadvantages are at least reduced so as to provide a more effective operational system and to also reduce the manufacturing and installation costs of the system. With this view in mind, it is proposed that the above described fuel injecting apparatus as proposed by this invention be incorporated in a fuel injection system for a multi-cylinder internal combustion engine, one such fuel injecting apparatus for each cylinder of the engine. Each fuel injecting apparatus is integrated with a single rigid elongated unitary member, the unitary member having a fuel supply duct and a gas supply duct formed therein extending in the direction of elongation of the unitary member, each fuel metering means being in direct communication with the fuel supply duct, each fuel cavity being located in the unitary member in communication with the gas supply duct, whereby when the port is open gas from the gas supply duct conveys fuel from the fuel cavity through the valve stem passage and the port cavity to and through the open port and into the cylinder. The above discussed construction incorporating a rigid elongated unitary member providing fuel and gas to a plurality of fuel injecting apparatus, each servicing a respective cylinder of a multi-cylinder engine, substantially reduces the number of fuel and gas lines required in the installation. In particular, only a single fuel supply line from the fuel pump and a single gas supply line from the pressurised gas source are required to service all of the fuel injecting apparatus. Apart from the substantially improved appearance which arises from this construction, the reduction in the number and length of resilient fuel and gas lines substantially reduces the effects on metering accuracy arising from variation in the cross-section of these lines with variation of the fluid pressure therein. In addition, the number of fuel and gas connections required to be made is substantially reduced, which contribute to both space savings and cost savings and to a reduction in the potential areas of leakage in the system. Further, it is possible by the use of a rigid elongated unitary member carrying a number of fuel injecting apparatus, one to be associated with each cylinder of the multi-cylinder engine, to use the rigid elongated unitary member as a holding down bar that clamps the fuel injecting apparatus in the required assembled relation with the respective cylinders of the engine. Each fuel injecting apparatus would have one end seated against the engine and in communication through a fuel delivery port in the one end with a respective cylinder of the engine, the opposite end portion of each fuel injecting apparatus being received in a respective recess in the rigid elongated unitary member, and means are provided to secure the unitary member to the engine with each fuel injecting apparatus clamped therebetween. Accordingly, the need to provide individual threaded holes for the securement of the respective fuel injecting apparatus to each cylinder is avoided, and a lesser number of threaded holes is required to hold the rigid elongated unitary member in clamping relation with the fuel injecting apparatus and the engine structure to maintain all of the fuel injecting apparatus in the required operating relationship to the engine. The invention will now be described with reference to the accompanying drawings, which depict one practical arrangement of a fuel injection system incorporating a fuel injecting apparatus, according to the present invention. In the drawings: Figure 1 is a perspective view of a typical three cylinder engine having a fuel injection system of the present invention fitted thereto; Figure 2 is a transverse sectional view of the fuel and gas rail at the location of a fuel metering and injecting unit; Figure 3 is an axial sectional view of fuel injecting unit and an adjoining portion of the fuel and gas rail; Figure 4 is a view of the air control ring in the direction 4-4 in Figure 2; Figure 5 is a sectional view of an engine cylinder head with the fuel and gas rail and the fuel metering and injecting units installed thereon; Figure 6 is a sectional view of a pressure regulator fitted to the fuel and gas rail; Figure 7 is a fragmentary sectional view of portion of the pressure regulator along the line 7-7 in Figure 6; and Figure 8 is a fragmentary sectional view of an alternative arrangement of directing the fuel and air into the fuel cavity. Referring now to Figure 1 of the drawings, the three cylinder two stroke cycle engine depicted therein is of basically conventional construction, having a cylinder block and crankcase unit 1, a detachable cylinder head 2, and an air induction system 4 on one side of the cylinder block and an exhaust system 5 on the opposite side of the block. Fitted to the cylinder head 2 are respective spark plugs 7, one for each cylinder of the engine. Extending generally centrally along the top of the cylinder head is the fuel and air rail unit 11 attached to the cylinder head by the mounting bolts 8. The fuel injection system for the engine as shown in Figure 2 comprises the air and fuel supply rail unit 11, with a metering unit 10 and an injecting unit 12 for each engine cylinder. The rail unit 11 is an extruded component with internal longitudinally extending air passage 13, fuel supply passage 14, and fuel return passage 15. These passages are closed at each end of the rail. At appropriate locations, as seen in Figure 1, there are provided an air supply conduit connector 9 communicating with the air passage 13, a fuel supply conduit connector 6 communicating with the fuel supply passage 14, and a fuel return conduit connector 3 communicating with the fuel return passage 15 via a pressure regulator as hereinafter described. The fuel metering unit 10 is a commercially available component and will not be described in detail herein. A suitable commercially available metering unit is that marketed by Rochester Products Division of General Motors Corporation under the Trade Mark "Multec". A fuel inlet port 16 and a fuel outlet port 17 are provided in the body 18 of the metering unit 10 to permit the flow of fuel therethrough, and a metering nozzle is provided in the area 19 to deliver fuel to the passage 20, as hereinafter described. The body 18 of the metering unit 10 is received within a lateral bore 26 provided in the external wall 21 of the rail unit 11, with an "O" ring seal 22 between the body 18 and the bore 26, and a further "O" ring seal 23 between the body 18 and the bore 27 in the internal wall 25 between the air passages 13 and fuel supply passage 14. The position of the nozzle area 19 of the metering unit 10 with respect to the passage 20 is controlled by the clamp plate 28 received in the recess 29 provided in the body 18. The clamp plate 28 is held against the wall 21 by a suitably located bolt or set screw (not shown). The body 18 of the metering unit passes through the wall between the passages 14 and 15 at 34 with a close tolerenced fit so fuel leakage therebetween is very restricted. The injecting unit 12 as seen in Figure 3 has a housing 30 with a cylindrical spigot 31 projecting from the lower end thereof with an injection port 32 therein communicating with an internal cavity 33. The poppet valve head 34, which co-operates with the port 32, is secured to the tubular valve stem 35. The tubular valve stem 35 is slidably supported in the cavity 33 by guide ribs 36 spaced equally about the periphery of the valve stem 35. The solenoid coil 40 is located in the housing 30 concentric with the tubular valve stem 35 and is retained between the base 37 of the housing 30 and the coverplate 38. The solenoid armature 41 affixed to the upper end of the tubular valve stem 35 has limited axial movement as indicated by the gap 39 and is urged in an upward direction by the spring 42 to normally maintain the valve head 34 in a closing relation with the port 32. The lower end of the valve stem 35 is provided with opposed apertures 43 to provide constant communication between the interior of the stem 35 and the cavity 33. Energising of the solenoid coil 40 draws the armature 41 downward to close the gap 39, thereby displacing the stem 35 and valve head 34 to open the port 32. The cover plate 38, being the upper end of the housing 30, is received in the bore 45 in the rail unit 11 so that the bore 48 at the upper end of the armature 41 receives the tube 46 mounted in the rail unit 11. The tube 46 is a sealed press fit in passage 20 formed in the wall 25, of the rail unit 11, and directs the fuel from the passage 20 into the open upper end of the valve stem 35. Attached to the end of the metering unit 10 which is located in the bore 27 in the wall 25 of the rail unit 11 is an air flow control ring 75. The annular flange 74 of the air flow control ring 75 fits over the metering unit body 18. In the external face of the flange 74 is an annular groove 77 which communicates with the passage 78, and via the series of apertures 79 with the interior cavity 80 of the ring 75. As seen in Figure 4 of the drawings, the end of the ring 75 has a central fuel passage 81 defined by the collar 82, which is secured to the peripheral portion of the ring 75 through the three equally spaced arms 84. The spaces defined between the periphery of the ring 75, the central collar 82 and the three arms 84 define three arcuate openings 85 for the flow of air from the air passage 13. As seen in Figure 2, the passage 88 communicates the air passage 13 with the annular cavity 80 about the collar 82 whereby air from the air passage 13 may pass through the passage 88 and the arcuate openings 85 and hence into the internal cavity 80 within the ring 75. This air can then pass adjacent the nozzle area 19 into the fuel passage 81 through the collar 82. It will thus be seen that when the fuel injection system is in operation, air may pass from the air passage 13 to establish a radially inward flow around the area 19 of the metering unit 10, from which the metered quantity of fuel is delivered, and that air will then move axially through the passage 81 into the passage 20 to then pass through the tube 46 into the hollow interior of the valve stem 35. This form of air flow will inhibit the loss of fuel by a back flow through the passage 88 into the air passage 13. The annular groove 77, apertures 79 and passage 78, provide a substantially unrestricted flow path for air from the air passage 13 into the bore 49 in the cover plate 38. From the bore 49, the air may enter the hollow valve stem 35 and also pass between the external surface of the armature 41 and the sleeve 47, through the gap 39 and into the cavity 33. This communication between the air passage 13 and the cavity 33 maintains an air flow and a pressure in the cavity 33 sufficient to prevent an accumulation of fuel in, or a back flow of fuel from, the cavity 33 past the armature 41 that could detract from the accuracy of the fuel metering to the engine. The sleeve 47 is outwardly flanged at 58 to seat on the base of the bore 49 in the cover plate 38. The lower end of the sleeve 47 is located between the neck 50 of the housing 30 and the extension 51 of the spigot 31. These three components are welded together in the area of overlapping relation to form a fuel and air tight junction. The apparatus as above described is intended to be used on a multi-cylinder engine as shown in Figure 1 with the single air and fuel rail unit 11 having assembled thereto a metering unit 10 and injecting unit 12 for each cylinder of the engine. As seen in Figure 5, the spigot 31 of the injecting unit 12 is received in an appropriate stepped bore 57 in the engine cylinder head 2 so that the fuel delivered through the port 32 will directly enter the cylinder combustion chamber 44. The seal ring 6, located in the spigot 31 will seal against an appropriate surface of the cylinder head. Suitable clamping arrangements, such as the bolts 8, are provided to secure the rail unit 11 to the cylinder head 2, so that the rail unit 11 is held in assembly with the injecting units 12, and the injecting units are in turn held in assembly with the cylinder head. The "O" ring 52 located in the bore 49 forms a seal between the rail unit 11 and the flange 58 of the sleeve 47 to prevent leakage of fuel or air between the rail unit 11 and the injecting unit 12. As can be seen in Figure 5, the engine cylinder head has coolant cavities and passages 53, 54 and 55, and a spark plug opening 56. The injection unit 12 received within a stepped bore 57, has part of the housing 30 disposed within the coolant cavity 54, so as to provide direct cooling of the injection unit to dissipate the heat generated by the solenoid coil 40 and to limit the transfer of heat from the combustion chamber to the injector unit and metering unit. In Figure 8, there is provided a modified construction of the air control ring 75 as described with reference to Figure 2. In the construction shown in Figure 8, the sleeve 110 and fuel guide tube 114 replace the fuel control ring 74 and collar 82. It is to be noted that the provision of the sleeve 110 is a modification to the previously disclosed construction. The sleeve 110 is a close fit, preferably a light interference fit in the bore 111 and the rail unit 11, with the portion 109 of the fuel metering unit 10 a close fit in the sleeve 110. The "O" ring 112 prevents leakage of fuel from the fuel supply passage 14. The delivery nozzle of the fuel metering unit 10 is located at 113, in alignment with the fuel guide tube 114 formed integral with the sleeve 110, and delivers the metered quantity of fuel into the fuel cavity 120. The fuel injecting unit 12 is in communication with the cavity 120 to receive the fuel therefrom and is of the same construction as previously described with reference to Figure 2. The cavity 120 is in communication with the air passage 13 via the bore 121, annular passage 122 surrounding the fuel guide tube 114, and the arcuate passage 124 therebetween. The bore 121 and the outer wall of the annular passage 122 are formed by respective parallel holes drilled prior to assembly of the fuel metering unit 10 and sleeve 110, and the arcuate passage 124 is formed by machining away portion of the wall between these two holes. As a result of these machining operations, the wall portion 125, between the two holes is retained and extends to over-lap part of the fuel guide tube 114, and a part conical surface 126 extending over an arc of 180° is formed. It is to be noted that the cavity 120, bore 121, annular passage 122 and arcuate passage 124 are individual to each metering and injecting units 10 and 12, where the fuel supply and return passage 14 and 15 and air supply passage 13 are common to all such units. The inclination of the surface 126 will direct fuel rebounding thereoff towards the injecting unit 12 rather than directly back towards the annular passage 122. In use, during a fuel injection phase, an air flow exists from the passage 13 through the bore 121, arcuate passage 124 and annular passage 122 into the cavity 120, and on through the cavity 120 to the fuel injecting unit 12. This air flow carries the fuel that has been delivered into the cavity 120, by the fuel metering unit 10, into and through the fuel injecting unit 12 to deliver it to the engine. It is not uncommon to deliver the fuel, or at least part thereof, into the cavity 120 prior to the commencement of the injection of fuel into the engine, that is at a time when there is substantially no air flow into the cavity 120 from the air passage 13. The above described arrangement of the bore 121 and passages 122 and 124 are such that a tortuous path is presented to any fuel that may otherwise have a tendency to flow back from the cavity 120 into the air passage 13. Also, fuel droplets rebounding off the surfaces of the cavity 120, after issuing from the metering unit 10, have a high probability of striking another wall of the cavity or of the annular passage 122, and so dissipate their kinetic energy and/or be directed on a path that will avoid escape of the fuel into the air passage 13. The use of an annular passage, as in annular passage 122, to provide the only point of entry of any fuel from the cavity 120 to a path to the air passage 13, has the advantage of providing a relatively unrestricted flow area for the air passing to the cavity but presents a narrow opening to fuel droplets passing in the reverse direction. The prevention of the escape of fuel from the cavity 20 in Figure 2 or 120 in Figure 8 to the air passage 13 has the advantage of improving the accuracy of metering the fuel to the engine with resultant improvements in fuel efficiency and emissions control of the engine, and avoidance of fuel accumulation in the air passage and the problem of purging thereof. As the fuel is delivered from the metering unit 10 into the passage 20 against the air pressure which exists therein, being substantially the pressure in the air passage 13, it is necessary to regulate the fuel pressure with respect to the air pressure to obtain the required accuracy in the metering of the fuel. As a plurality of metering and injecting units are incorporated in the single rail unit 11, the provision of a single regulator, also incorporated into the rail unit 11, can provide the required pressure regulation for all metering and injecting units. A typical construction of a regulator unit is depicted in Figure 6 of the accompanying drawings. The regulator unit 60 comprises a body 61 having a fuel portion 62 and an air portion 63 secured together by the swaged flange 64. The fuel portion 62 is a close fit in the bore 56 that extends through the external wall 21 of the rail unit 11 and also through the wall 74 between the fuel supply passage 14 and the fuel return passage 15. The fuel return passage 15 communicates with the hollow interior of the fuel portion 62 through apertures 59 in the peripheral wall of the fuel portion 62. An "O" ring seal 65 is provided between the fuel portion 62 of the body 61 and the wall of the rail unit 11. The fuel portion 62 also extends partly into the wall 25 between the fuel supply passage 14 and the air passage 13 with the air portion 63 extending through the remainder of the wall 25 into the air passage 13. The diaphragm 66 is clamped between opposite shoulders on the fuel portion 62 and air portion 63 so as to form a barrier between the fuel and the air, but may flex in the normal manner of a diaphragm. The pre-load spring 67 acts against the pressure plate 68 secured to the diaphragm 66 and the force applied by the spring can be controlled by the adjusting plug 69, which has an aperture therethrough to communicate the air passage 13 with the interior of the air portion 63. The pressure plate 68 carries a valve disc 70, which co-operates with the port sleeve 71, which defines the port 72. The body 61 is provided with a suitable threaded aperture 73 to which a fuel return connector 3 may be fitted to return released fuel to a fuel reservoir. As seen in more detail in Figure 7, the valve disc 70 may be of a form having an integral spherical head 90 received in a conical cavity 91 in the pressure plate 68. The head 90 is held in assembly by the retainer plate 92, that is secured about the periphery by the swaged rim 93 of the pressure plate 68. The retainer plate 92 has a slot extending to the periphery thereof from the central opening 94 to permit entry of the neck portion 95 into the central opening 94. The spring 96 urges the spherical head 90 toward the retainer plate 92 to maintain the central location of the valve disc 70. This construction improves the accuracy of the sealing of the valve disc 70 with the port sleeve 71. It is to be understood that the construction of the regulator above described may be varied by having the port sleeve 71 attached to the diaphragm 66 and the valve disc stationary. In use, if the fuel pressure remains below the pressure represented by the combined affect of the air pressure on the diaphragm 66 and the load applied by the spring 67, the valve plate 70 will remain in the position as shown closing the port 72. However, if the fuel pressure rises to a level sufficient to overcome the combined load of the air pressure and spring 67 on the diaphragm 66, then the diaphragm will deflect to the right as shown in the drawing, thereby displacing the valve disc 70 to open the port 72. The fuel released through the port 72 is returned to the fuel reservoir. The above described construction results in the regulator device being substantially contained within the confines of the rail unit 11 and thus does not in real terms contribute to an increase in the overall dimensions of the engine and fuel injection system. Also, in this construction, the volume of fuel within the rail unit damps the pressure fluctuations arising from the operation of the regulator. It is to be understood that the fuel injection system as above described may be used in respect of any form of internal combustion engine, including engines operating on either the four stroke or two stroke cycle. Such engines incorporating the fuel injection system above described are particularly suitable for use in all forms of vehicle engines, including engines for aircraft, land vehicles and marine applications, the latter including outboard marine engines.

Claims: An apparatus (12) for injecting fuel to an internal combustion engine, comprising: a body having therein a fuel cavity (80) communicating with a port cavity (33), metering means (10) to selectively deliver fuel to the fuel cavity (80), a port (32) in the body providing communication between the port cavity (33) and the exterior of the body, valve means (34, 35) including a valve element (34) adapted to co-operate with the port (32) to selectively open and close the port (32) and a valve stem (35) attached to the valve element (34); selectively operable electromagnetic means (40, 41) within the body operably connected to the valve stem (35) to move the valve element (34) to open and close the port (32); and means to supply gas to the fuel cavity (80) at least when the port (32) is open to convey fuel from the fuel cavity (80) to and through the open port (32), characterised by the valve stem (35) extending from the port cavity (33) to the fuel cavity (80) through the electromagnetic means (40, 41) and a passage (20) extending through the valve stem (35) communicating the port cavity (33) with the fuel cavity (80), whereby the fuel from the fuel cavity (80) is delivered entrained in said gas through the valve stem passage (20) and the port cavity (33) to and through the open port (32). A fuel injecting apparatus (12) as claimed in claim 1, wherein the electromagnetic means (40, 41) comprises a stationary solenoid coil (40) located concentrically about the valve stem (35) and an armature (41) secured to the valve stem (35). A fuel injecting apparatus (12) as claimed in claim 2, wherein the armature (41) is located substantially within an annular space (39) formed between the valve stem (35) and the solenoid coil (40). A fuel injecting apparatus (12) as claimed in claim 1, wherein the valve stem (35) is hollow and has an aperture (43) in the wall thereof adjacent the valve element (34) to permit fuel to pass from the interior of the hollow valve stem (35) into the port cavity (33). A fuel injection system for an internal combustion engine, having an apparatus (12) as claimed in any one of claims 1 to 4 for injecting fuel to the internal combustion engine. A fuel injection system for a multi-cylinder internal combustion engine, comprising for each cylinder (44) of the engine a fuel injecting apparatus (12) as claimed in claim 1 arranged to deliver fuel to the cylinder (44) through the port (32) provided in the body (30) of the fuel injecting apparatus (12), each fuel injecting apparatus (12) being integrated with a single rigid elongated unitary member (11), the unitary member (11) having a fuel supply duct (14) and a gas supply duct (13) formed therein extending in the direction of elongation of the unitary member (11), each fuel metering means (10) being in direct communication with the fuel supply duct (14), each fuel cavity (80) being located in the unitary member (11) in communication with the gas supply duct (13), whereby when the port (32) is open gas from the gas supply duct (13) conveys fuel from the fuel cavity (80) through the valve stem passage (20) and the port cavity (33) to and through the open port (32). A fuel injection system as claimed in claim 6, characterised by a conduit (81) within the unitary member (11) extending from the fuel metering means (10) to the fuel cavity (80), the conduit (81) being located so the metered quantity of fuel passes from the fuel metering means (10) through the conduit (81) into the fuel cavity (80). A fuel injection system as claimed in claim 7, characterised by the gas supply duct (13) communicating with the conduit (81) adjacent the location (19) of the entry of the fuel to the conduit (81) so that gas passes through the conduit (81) to enter the fuel cavity (80). A fuel injection system as claimed in claim 7 or 8, characterised by the conduit (81) extending through an opening in the wall of the fuel cavity (80), the conduit (81) defining with the opening an annular passage (85) about the conduit, the annular passage (85) providing communication between the gas supply duct (13) and the fuel cavity, whereby gas flows through the annular passage (85) into the fuel cavity (80). A fuel injection system as claimed in claim 7 or 8, characterised by the configuration of the fuel cavity (120) being arranged to present an inclined face (126) opposite the location (114) of the entry of the fuel into the fuel cavity (120), the face (126) being inclined to the trajectory of the incoming fuel so the fuel rebounding from the inclined face (126) is directed to enter the valve stem passage (20). A fuel injection system as claimed in any one of claims 6 to 10, characterised by each fuel injecting apparatus (12) being mounted to the unitary member (11) with the body (30) projecting from one external wall of the unitary member (11) and the fuel metering means (10) projecting from another external wall of the unitary member (11) in a direction inclined to the direction of projection into the unitary member (11) of the body(30) of the fuel injecting apparatus (12). A fuel injection system as claimed in claim 11, characterised by the body (30) of each fuel injecting apparatus (12) projecting in a direction at right angles to the direction that the fuel metering means (10) projects into the unitary member (11). A fuel injection system as claimed in any one of claims 6 to 10, characterised by the body (30) of each fuel injecting apparatus (12) having the end portion thereof remote from the port (32) received in a respective recess (45) in the rigid elongated unitary member (11), the recesses (45) being arranged so the bodies (30) are spaced from each other in the direction of elongation of the unitary member (11), the end of each body (30) in which the port (32) is located being seated against the engine with the port (32) therein in communication with a respective cylinder (44) and means (8) securing the unitary member (11) to the engine so the bodies (30) are clamped therebetween. A fuel injection system for a multi-cylinder internal combustion engine, comprising for each cylinder (44) of the engine a fuel injecting apparatus (12) as claimed in claim 1, the body (30) of each fuel injecting apparatus (12) having the end portion thereof remote from the port (32) received in a respective recess (45) in a rigid elongated unitary member (11) so the bodies (30) are spaced from each other in the direction of elongation of the unitary member (11), the opposite end of each body (30) seated against the engine with the port (32) therein communicating with a respective cylinder (44) of the engine, and means (8) securing the unitary member (11) to the engine so the bodies (30) are clamped therebetween. A fuel injection system as claimed in any one of claims 6 to 10, characterised by pressure regulator means (60) mounted to extend into the unitary member (11) to communicate with the gas supply duct (13) and the fuel supply duct (14) the pressure regulator means (60) being adapted to in use maintain a predetermined pressure differential between the gas in the gas supply duct (13) and the fuel in the fuel supply duct (14). A fuel injection system as claimed in claim 11, characterised by pressure regulator means (60) mounted to extend into the unitary member (11) to communicate with the gas supply duct (13) and the fuel supply duct (14) the pressure regulator means (60) being adapted to in use maintain a predetermined pressure differential between the gas in the gas supply duct (13) and the fuel in the fuel supply duct (14). A fuel injection system for a multi-cylinder internal combustion engine, comprising for each cylinder (44) of the engine a respective fuel injecting apparatus (12) as claimed in claim 1, each fuel injecting apparatus (12) having one end seated against the engine and in communication through a fuel delivery port (32) in the one end with a respective cylinder (44) of the engine, the opposite end portion of each fuel injecting apparatus (12) being received in a respective recess (45) in a rigid elongated unitary member (11), and means (8) securing the unitary member (11) to the engine with each fuel injecting apparatus (12) clamped therebetween. A fuel injection system according to claim 17, wherein the unitary member (11) has a fuel supply duct (14) and a gas supply duct (13) formed therein extending in the direction of elongation of the unitary member (11), the opposite end portion of each fuel injecting apparatus (12) being in communication with the gas supply duct (13). A fuel injection system according to claim 18, wherein each fuel injecting apparatus (12) has a respective fuel metering means (10) in communication with the fuel supply duct (14). A fuel injection system according to claim 17, wherein the unitary member (11) has a fuel supply duct formed therein extending in the direction of elongation of the unitary member (11).

Inventors: LEAR MARK, LEIGHTON SAM RUSSELL, SAYER CHRISTOPHER NEVILLE FRAN, THOMPSON IAN REGINALD, LEAR, MARK, LEIGHTON, SAM RUSSELL, SAYER, CHRISTOPHER NEVILLE FRANCIS, THOMPSON, IAN REGINALD
Applicants: ORBITAL ENG PTY, ORBITAL ENGINE COMPANY (AUSTRALIA) PTY. LTD.
Application year: 1988
Main classification: F02M67
IPC codes: F02M51, F02M61, F02M67, F02B75, F02M55, F02M69, F02B61