Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B19/00—Engines characterised by precombustion chambers
  • F02B19/02—Engines characterised by precombustion chambers the chamber being periodically isolated from its cylinder
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B19/00—Engines characterised by precombustion chambers
  • F02B19/10—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder
  • F02B19/1019—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder with only one pre-combustion chamber
  • F02B19/109—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder with only one pre-combustion chamber with injection of a fuel-air mixture into the pre-combustion chamber by means of a pump, e.g. two-cycle engines
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
  • F02M47/04—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure using fluid, other than fuel, for injection-valve actuation
  • F02M47/046—Fluid pressure acting on injection-valve in the period of injection to open it
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M57/00—Fuel-injectors combined or associated with other devices
  • F02M57/02—Injectors structurally combined with fuel-injection pumps
  • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
  • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M57/00—Fuel-injectors combined or associated with other devices
  • F02M57/06—Fuel-injectors combined or associated with other devices the devices being sparking plugs
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
  • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
  • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
  • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
  • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
  • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02P—IGNITION, OTHER THAN COMPRESSION IGNITION, FOR INTERNAL-COMBUSTION ENGINES; TESTING OF IGNITION TIMING IN COMPRESSION-IGNITION ENGINES
  • F02P13/00—Sparking plugs structurally combined with other parts of internal-combustion engines
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B19/00—Engines characterised by precombustion chambers
  • F02B19/10—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder
  • F02B19/1019—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder with only one pre-combustion chamber
  • F02B19/108—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder with only one pre-combustion chamber with fuel injection at least into pre-combustion chamber, i.e. injector mounted directly in the pre-combustion chamber
  • F02B19/1085—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder with only one pre-combustion chamber with fuel injection at least into pre-combustion chamber, i.e. injector mounted directly in the pre-combustion chamber controlling fuel injection
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B19/00—Engines characterised by precombustion chambers
  • F02B19/12—Engines characterised by precombustion chambers with positive ignition
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
  • F02M2547/006—Springs assisting hydraulic closing force
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M2700/00—Supplying, feeding or preparing air, fuel, fuel air mixtures or auxiliary fluids for a combustion engine; Use of exhaust gas; Compressors for piston engines
  • F02M2700/13—Special devices for making an explosive mixture; Fuel pumps
  • F02M2700/1317—Fuel pumpo for internal combustion engines
  • F02M2700/1376—Fuel pump with control of the pump piston stroke
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
  • F02M69/04—Injectors peculiar thereto
  • F02M69/042—Positioning of injectors with respect to engine, e.g. in the air intake conduit
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
  • Y02T10/00—Road transport of goods or passengers
  • Y02T10/10—Internal combustion engine [ICE] based vehicles
  • Y02T10/12—Improving ICE efficiencies

Definitions

• the present invention relates to a hydraulic cam injection system provided inter alia for injecting a pilot charge consisting of a mixture of air and easily flammable fuel in a valve ignition prechamber or, more incidentally , in a prechamber formed by a shuttle electrode spark plug.
• said prechamber When said pilot charge is ignited by a spark, said prechamber ejects hot gas torches into the combustion chamber of an internal combustion heat engine in order to ignite a main charge contained in said chamber.
• No. 18 58111 relates to a magnetic valve return device.
• the second said request was registered on May 13, 2019 under number 1904961 and concerns an ignition insert with active prechamber.
• the highly diluted main charge increases the average and / or maximum thermodynamic efficiency of said engine which receives it compared to that of engines with ignition by spark plug only and therefore, reduces the fuel consumption of said engine at the same work produced.
• said injector must be as compact as possible to be able to be integrated into the cylinder head of any spark ignition reciprocating engine without unduly interfering with the intake ducts, with the exhaust ducts, or with the chambers of cooling water included in said cylinder head.
• said injector should advantageously have a nozzle of great length and small diameter.
• This particular configuration is necessary so that said injector can be integrated into the cylinder head of any reciprocating internal combustion engine with spark ignition without interfering in a crippling manner with the components and functional volumes of said cylinder head.
• the injector in question must also offer high dynamics and high permeability. These qualities are necessary to be able to inject the pilot charge into the prechamber within the allotted time, regardless of the speed and load of the internal combustion engine, and despite a relatively expected pressure of the air and fuel mixture. low at the inlet of said injector.
• the temperature of the injector does not exceed one hundred degrees Celsius and if the richness of the air-gasoline mixture that it injects is 1.2 or 1.3 , the pressure of said mixture at the inlet of said injector must not exceed fifty bars.
• the most suitable solution is to significantly increase the stroke of the injector needle, compared to that of a direct automotive gasoline injector which is of the order of fifty to sixty micrometers.
• the problem is that increasing the needle stroke requires more than proportionally increasing the size and power of the solenoid actuator that moves said needle. In fact, raising the needle more within the same time period increases the average speed of lifting and resting said needle. This increase in lift and rest speed has more impact on the sizing of the solenoid actuator as the reciprocating internal combustion engine itself is running at high speed.
• an increased stroke of said needle moves away the solenoid pallet which actuates said needle from the stator with which said pallet cooperates.
• the constituent coil of the solenoid actuator must produce a very strong magnetic field. This is all the more true as the needle moves away strongly from its seat, it is necessary to provide a powerful return spring, capable of returning said needle to its seat within the allotted time.
• the hydraulic cam injection system according to the invention can in particular
• the hydraulic cam injection system comprises:
• At least one injection valve which comprises a valve stem and which ends in a tulip, the latter exposing a valve sealing surface, said valve being wholly or partly housed in a tubular injection nozzle terminated by an injection valve seat on which the valve sealing face can sealingly rest while a space is left between the valve stem and the internal surface of the tubular injection nozzle to let circulate an injectable fluid pressurized by pressurizing means;
• At least one slave cylinder which is directly or indirectly integral with the end of the tubular injection nozzle
• At least one receiving piston integral with the valve stem and housed in the receiving cylinder said piston being able to move in longitudinal translation in said cylinder and having an axial face on the injectable fluid side which communicates with the internal volume of the nozzle. tubular injection, and an axial face on the hydraulic fluid side which forms, with the receiving cylinder, a receiving chamber of variable volume filled with hydraulic fluid;
• At least one hydraulic fluid supply device connected to the receiving chamber and which makes it possible to actuate the receiving piston via the hydraulic fluid through a hydraulic action line.
• the hydraulic cam injection system comprises a receiving piston return spring which tends to move the receiving piston closer to a receiving cylinder head.
• the hydraulic cam injection system comprises permeable guide means which are directly or indirectly integral with the injection valve and / or the tubular injection nozzle, said means keeping the valve d injection approximately centered in the tubular injection nozzle.
• the hydraulic cam injection system comprises a hydraulic fluid supply device which consists of an injection cam which has at least one cam profile maintained directly or indirectly in contact with an axial action face presented by a sender piston housed in a sender cylinder, said piston having - opposite the axial action face - an axial hydraulic fluid emission face which forms an emitter chamber with the cylinder transmitter however that the cam profile can move the transmitter piston in longitudinal translation in the transmitter cylinder when the injection cam is rotated by a driving source.
• the hydraulic cam injection system comprises a hydraulic action conduit which connects the emitting chamber to the receiving chamber, said conduit, the emitting chamber and the receiving chamber being filled with hydraulic fluid.
• the hydraulic cam injection system comprises a the cam profile which comprises at least one angular lift sector which moves the emitter piston when said sector is in contact with the axial action face and the injection cam is rotating, and at least one angular sector of circular maintenance and centered on the axis of rotation of said injection cam which immobilizes the emitter piston when said sector is in contact with the axial action face and this despite the injection cam being in rotation.
• the hydraulic cam injection system comprises a cam profile which is maintained in contact with the axial action face by means of a rocker arm which directly or indirectly bears on a housing of cam in which the injection cam rotates.
• the hydraulic cam injection system comprises a rocker arm which bears on the cam housing by means of a movable tipping point whose position between the cam profile and the axial face of The action can be changed by an injector lift actuator.
• the hydraulic cam injection system comprises a movable tipping point which consists of a movable support roller which can roll or slide on a movement track provided in the cam housing, said roller cooperating with a tilting track arranged at the back of the rocker.
• the hydraulic cam injection system comprises a movable support roller receives at each of its ends a pinion
• said pinions being integral in rotation, while each said pinion cooperates with an orientation rack integral with the cam housing.
• the hydraulic cam injection system comprises a movable support roller which receives a worm wheel which cooperates with a worm whose axial position is fixed relative to the cam housing, said screw being able to be driven in rotation by G injector lift actuator.
• the hydraulic cam injection system comprises a movable support roller which receives a thread in which G injector lift actuator can rotate a displacement screw which is integral in position of the housing. cam but free to rotate around its longitudinal axis.
• the hydraulic cam injection system comprises an injection cam phase shifter which is interposed between the injection cam and the driving source.
• the hydraulic cam injection system comprises a tubular injection nozzle, the end of which ends with the injection valve seat is capped with a diffuser with holes.
• the hydraulic cam injection system comprises a diffuser with holes, at least part of its internal wall of which is cylindrical and leaves a small clearance between itself and the external peripheral surface of the tulip so that said diffuser forms the permeable guide means.
• the hydraulic cam injection system comprises a booster pump which tends to introduce hydraulic fluid into the hydraulic action duct via a booster non-return valve, said hydraulic fluid coming from a hydraulic fluid tank.
• the hydraulic cam injection system comprises at least one drainage orifice which is connected to a drainage duct and which opens into the receiving cylinder, the axial face on the injectable fluid side and the axial face on the fluid side. hydraulic always remaining axially positioned on either side of said orifice whatever the position of the receiving piston.
• the hydraulic cam injection system comprises a receiving piston which has a drainage groove which communicates with the drainage port.
• the hydraulic cam injection system comprises a receiving piston which consists of a first body which receives the axial face on the injectable fluid side and which is integral with the valve stem, and of a second body which may or may not be integral with said first body and which receives the axial face on the hydraulic fluid side, an external shoulder arranged on one, the other or both of said bodies forming the drainage groove.
• the hydraulic cam injection system comprises a maximum range of displacement of the tilting point movable between the cam profile and the axial action face which is determined by at least one end stop .
• the hydraulic cam injection system comprises a displacement track which is secured to the cam housing by means of at least one track orienting ball.
• the hydraulic cam injection system comprises a receiving piston which consists of at least a first body which receives the axial face on the injectable fluid side and which is integral with the valve stem, and of at least one second body, whether or not integral with said first body and which receives the axial face on the hydraulic fluid side.
• the hydraulic cam injection system comprises a receiving piston which comprises an external shoulder arranged on one, the other or both bodies, said shoulder forming a drainage groove which communicates with at least a drainage orifice which is provided in the receiving cylinder and which is connected to a drainage duct.
• FIG.l is a schematic sectional view of the hydraulic cam injection system according to the invention as it can be installed in the cylinder head of an internal combustion engine equipped with a prechamber of valve ignition according to French patent application N ° FR 17 50264, and an active prechamber ignition insert according to French patent application N 3 060 222.
• FIG.2 is a schematic sectional view which shows the angular lifting and holding sectors as can be accommodated by the cam profile of the hydraulic cam injection system according to the invention.
• FIG. 3 to 5 are schematic sectional views illustrating the operation of the injection cam and of the sender piston of the hydraulic cam injection system according to the invention, said cam cooperating with a rocker arm, the lever arm of which can vary by function of the position of a displaceable support roller, said position being controlled by an electric stepper motor via a worm and a worm wheel.
• FIG.6 is a three-dimensional view of the injection cam of the hydraulic cam injection system according to the invention, and of the main functional components shown in Figures 3 to 5 with which said cam cooperates.
• FIG.7 is a three-dimensional view of the tubular injection nozzle of the system
• hydraulic injection cam according to the invention, and the main components that it houses or with which it cooperates.
• FIG.8 is a three-dimensional sectional view of the tubular injection nozzle of the hydraulic cam injection system according to the invention, and of the main components that it houses or with which it cooperates.
• FIG.9 is a three-dimensional view of the injection valve of the hydraulic cam injection system according to the invention, equipped with the receiving piston and the receiving piston return spring.
• FIG.10 is a three-dimensional view of the hole diffuser as it may be provided to complete the tubular injection nozzle of the hydraulic cam injection system according to the invention.
• FIG.l 1 is a schematic sectional view of the tubular injection nozzle of the hydraulic cam injection system according to the invention and of the main components that it hosts or with which it cooperates, such as 'it can be installed in the cylinder head of an internal combustion engine equipped with a valve pre-chamber according to French patent application No. FR 17 50264, and an ignition insert with active pre-chamber according to French patent application N 3 060 222.
• FIG.12 is a three-dimensional phantom view of the injection cam of the hydraulic cam injection system according to the invention, the displaceable support roller of which receives a thread in which the lifting actuator of injector can rotate a displacement screw.
• FIG. 1 to 12 There is shown in Figures 1 to 12 the hydraulic cam injection system 100 according to the invention, various details of its components, its variants, and its accessories.
• Hydraulic cam 100 includes at least one injection valve 50 which includes a valve stem 51, and which terminates in a tulip 52 which exposes a valve seal face 53.
• valve 50 is fully or partially housed in a tubular injection nozzle 54 terminated by an injection valve seat 55 on which the valve sealing face 53, while a space is left between the valve stem 51 and the internal surface of the tubular injection nozzle 54 to allow an injectable fluid 58 to circulate under pressure by pressurizing means 10.
• valve sealing surface 53 may be frustoconical while the injection valve seat 55 is conical.
• the hydraulic cam injection system 100 provides permeable guide means 56 which are directly or indirectly integral with the injection valve 50 and / or the tubular injection nozzle 54. Said means 56 keep the injection valve 50 approximately centered in the tubular injection nozzle 54 regardless of the axial position of said valve 50 relative to said nozzle 54.
• the injectable fluid 58 may circulate between the injection valve 50 and the tubular injection nozzle 54.
• the hydraulic cam injection system 100 comprises a nozzle inlet port 59 arranged in the tubular injection nozzle 54 and through which the injectable fluid 58 is introduced inside said nozzle 54 after having been conveyed by an injectable fluid supply duct 66 which connects the pressurizing means 10 to said orifice 59.
• connection between the injectable fluid supply duct 66 and the nozzle inlet orifice 59 can be made by welding, crimping, by means of a "banjo" connector known per se, or by using a terminal block of any type.
• the injectable fluid supply duct 66 can receive heating means by electrical resistance, by external circulation of a heat transfer fluid such as water or oil, or by any other means. . Said heating means advantageously make it possible to accelerate the rise in temperature of the injectable fluid supply duct 66 when the hydraulic cam injection system 100 according to the invention is started up in a low temperature environment.
• Said means or similar means can also be applied to the hydraulic action conduit 78 and / or to the tubular injection nozzle 54.
• the hydraulic cam injection system 100 comprises at least one receiver cylinder 61 which is directly or indirectly secured to the end of the tubular injection nozzle 54 which is located opposite the end of said nozzle 54 which receives the injection valve seat 55, said receiver cylinder 61 being positioned in the extension of said nozzle 54.
• Figures 1, 8, 9 and 11 show that the hydraulic cam injection system 100 comprises at least one receiver piston 62 integral with the valve stem 51 and housed in the receiver cylinder 61, said piston 62 able to move in longitudinal translation in said cylinder 61 and having an axial face on the injectable fluid side 63 which communicates with the internal volume of the tubular injection nozzle 54, and an axial face on the hydraulic fluid side 64 which forms, with the receiver cylinder 61 and a receiving cylinder head 74 which terminates said cylinder 61, a receiving chamber 71 of variable volume.
• the receiving piston 62 can be made in one or more parts, and that it can receive a seal of any type whatsoever and in particular, a composite seal having a low coefficient of friction and a high abrasion resistance. This particular configuration can also be applied to the emitter piston 69.
• the hydraulic cam injection system 100 comprises a hydraulic fluid supply device 65 consisting of at least one injection cam 67 which has at least a cam profile 68 maintained directly or indirectly in contact with an axial action face 75 presented by a sender piston 69 housed in a sender cylinder 70.
• said piston 69 has - opposite the axial action face 75 - an axial hydraulic fluid emission face 76 which forms a emitter chamber 72 with the emitter cylinder 70 and an emitter cylinder head 77 which terminates said cylinder 70, while the cam profile 68 can move the emitter piston 69 in longitudinal translation in the emitter cylinder 70 when the injection cam 67 is activated. rotation by a motor source 73.
• the driving source 73 can take the form of an electric motor, a hydraulic motor, the crankshaft of an internal combustion engine 2, or any other driving source 73 to which the injection cam 67 is connected by any type of transmission whether it is a shaft, a toothed belt or not, a chain, or pinions.
• injection cam 67 is driven by the crankshaft of an internal combustion engine 2, it can be integral with the camshaft of said engine 2, or placed at the end of the central shaft of an air compressor which forms the pressurizing means 10, or receive a clean pulley which is driven by the distribution belt of said engine 2.
• the hydraulic cam injection system 100 comprises at least one hydraulic action conduit 78 which connects the emitting chamber 72 to the receiving chamber 71, said conduit 78, the emitting chamber 72 and the receiving chamber 71 being filled with hydraulic fluid 60.
• FIGS 8, 9 and 11 illustrate that a receiver piston return spring 79 can be provided which tends to bring the receiver piston 62 of the receiver cylinder head 74 which has the consequence of tending to maintain the range of valve seal 53 in contact with the injection valve seat 55.
• Said spring 79 may for example be housed in the receiving cylinder 61 and / or in the tubular injection nozzle 54 and be helical, formed of a stack of elastic washers or be of any type known to those skilled in the art. art. Note that a similar return spring may tend to bring the emitter piston 69 closer to the emitting cylinder head 77.
• the cam profile 68 may include at least one angular lift sector 15 which moves the emitter piston 69 when said sector 15 is in contact with the axial action face 75 and that the injection cam 67 is rotating, and at least one angular retaining sector 16 circular and centered on the axis of rotation of said injection cam 67 which immobilizes the emitter piston 69 when said sector 16 is in contact with the axial action face 75 and this despite the injection cam 67 being in rotation.
• the profile of cam 68 can be kept in contact with the axial action face 75 by means of a rocker arm 80 which bears directly or indirectly on a cam housing 81 in which the injection cam 67 rotates.
• rocker arm 80 can be kept in contact with the cam profile 68 by
• rocker arm 80 can be kept in contact. either of the cam profile 68 or of the axial action face 75 by a rocker arm return spring 14.
• rocker arm 80 can cooperate with guide means, not shown, arranged in the cam housing 81 so that said rocker arm 80 cannot rotate about an axis perpendicular to its operational tilting axis.
• the movable tipping point 82 may consist of a movable support roller 84 which can roll or slide on a displacement track 85 arranged in the cam housing 81, said roller 84 cooperating with a tilting track 87 arranged at the back of the rocker arm 80.
• the rocker arm 80 can be articulated around a ball 88 integral with the axial action face 75.
• the latch roller 86 may have an outer shape in barrel.
• the displacement track 85 and the tilting track 87 can be perfectly flat and the displaceable support roller 84 can be perfectly cylindrical. This non-limiting configuration makes it possible to avoid any hyperstatic relationship between the various parts 84, 85, 86, 87 which have just been listed, while avoiding having to produce a cam profile 68 whose outer axial surface is curved. .
• FIG. 6 clearly shows that the movable support roller 84 can receive at each of its ends an orientation pinion 89, said pinions 89 being so lidaires in rotation, while each said pinion 89 cooperates with a rack d 'orientation 90 integral with the cam housing 81.
• This particular configuration makes it possible to keep the movable support roller 84 perpendicular to the displacement track 85 with which it cooperates, and this regardless of the position of said roller 84 relative to said track 85.
• Figure 6 also clearly shows that the movable support roller 84 can receive a worm wheel 91 which cooperates with a worm 92 whose axial position is fixed relative to the cam housing 81.
• said screw 92 can be rotated by the injector lift actuator 83 which can be, as shown in Figure 1 and Figures 3 to 6, an electric stepper motor 93 matched or not with 'a reduction gear of any type and controlled by an ECU computer.
• step-by-step electric motor 93 can be connected to the worm 92 directly or by means of a transmission by belt, chain, pinions, or any type known to those skilled in the art.
• the injector lift actuator 83 rotates the worm 92
• the movable support roller 84 moves relative to the displacement track 85 with which it cooperates, which has the consequence of moving the position of the movable bottom point 82 relative to the cam housing 81. This adjusts the amount of injectable fluid 58 expelled from the tubular injection nozzle 54.
• the movable support roller 84 can receive a thread in which the injector lift actuator 83 can rotate a displacement screw 17 which is integral in position of the housing cam 81 but free to rotate around its longitudinal axis, which has the effect of sliding the movable support roller 84 on the displacement track 85.
• an injection cam phase shifter 96 can be interposed between the injection cam 67 and the driving source 73, said phase shifter 96 making it possible to advance or angularly delay with respect to the driving source 73 the movement which the injection cam 67 impresses on the emitting piston 69, for example when said source 73 consists of the crankshaft of an engine with an internal combustion engine 2.
• injection cam phase shifter 96 may be similar to that of hydraulic or electric camshaft phase shifters in automotive internal combustion engines.
• At least part of the internal wall of the diffuser with holes 94 can be cylindrical and leave a small clearance between itself and the external peripheral surface. of the tulip 52 so that said diffuser 94 forms the permeable guide means 56.
• FIG. 1 shows that a booster pump 7 can be provided which tends to introduce hydraulic fluid 60 into the hydraulic action duct 78 via a booster check valve 8, said hydraulic fluid 60 from a hydraulic fluid tank 11.
• the booster pump 7 may consist of the lubricating pump of an internal combustion engine 2 while the hydraulic fluid tank 11 consists of the oil pan of said engine 2.
• the hydraulic action conduit 78 may include a pressure limiter and purge devices known per se.
• the hydraulic cam injection system 100 can receive at least one drainage orifice 97 which is connected to a drainage duct 99 and which opens into the cylinder. receiver 61. It is understood that in this case, the axial face on the injectable fluid side 63 and the axial face on the hydraulic fluid side 64 always remain axially positioned on either side of said orifice 97 regardless of the position of the receiver piston 62.
• the receiving piston 62 comprises a drainage groove 98 which communicates with the drainage orifice 97, said groove 98 collecting, on the one hand, injectable fluid 58 leaking between the receiving piston 62 and the cylinder.
• receiver 61 from the axial face on the injectable fluid side 63 and, on the other hand, of the hy- fluid 60 and / or air leaking between said piston 62 and said cylinder 61 from the hydraulic fluid side axial face 64, so that said injectable fluid 58, said hydraulic fluid 60 and / or said air can be exhausted via the drainage pipe 99.
• the receiving piston 62 may consist of a first body which receives the axial face on the injectable fluid side 63 and which is integral with the valve stem 51, and of a second integral body or not of said first body and which receives the axial face on the hydraulic fluid side 64, an external shoulder 20 arranged on one, the other or both of said bodies forming the drainage groove 98.
• the maximum range of displacement of the movable tilting point 82 between the cam profile 68 and the axial action face 75 can advantageously be determined by at least one end stop 19 which constitutes among other things a geometric reference position that can be used by the injector lift actuator 83 to reset the position of the movable tilting point 82, and to adjust the correct quantity of injectable fluid 58 expelled from the tubular injection nozzle 54 via the passage left between the valve sealing face 53 and the injection valve seat 55.
• FIG. 12 also illustrates that the displacement track 85 can be made
• valve ignition prechamber which was the subject of French patent application N ° FR 17 50264, said prechamber receiving on the one hand, the valve magnetic return device which is the subject of French patent application N ° 18 58111 , and on the other hand, the ignition insert with active prechamber which is the subject of French patent application No. 1904961.
• FIGS 1 and 11 show the hydraulic cam injection system 100 which according to this non-limiting example is fitted to an internal combustion engine 2 which comprises in particular a cylinder 4 topped with a cylinder head 3, said cylinder 4 and said cylinder head 3 forming, with a piston 31, a combustion chamber 5.
• an internal combustion engine 2 which comprises in particular a cylinder 4 topped with a cylinder head 3, said cylinder 4 and said cylinder head 3 forming, with a piston 31, a combustion chamber 5.
• valve ignition prechamber 1 arranged in an active prechamber ignition insert 6 housed in the cylinder head 3. It is also noted in said Figures 1 and 11 that the nozzle of tubular injection 54 and the injection valve 50 open into the valve ignition prechamber 1 in order to be able to introduce therein an injectable fluid 58 which, according to this example, consists of an AF mixture of air and gasoline easily flammable.
• Said AF mixture forms a pilot charge 9 which is intended to be ignited by an ignition plug 12 which opens into the valve ignition prechamber 1. Once fired, said pilot charge 9 will be ejected. via gas ejection orifices 24 in the combustion chamber 5, in the form of high temperature gas torches. Said torches are intended to ignite a main charge 30 contained in said combustion chamber 5.
• valve ignition prechamber 1 and the combustion chamber 5 are separated by a valve 13 which is returned to its seat by a permanent magnet 49 which is part of the control device.
• magnetic return valve 42 as described in French patent application No. 18 58111 belonging to the applicant.
• Said valve 13 allows the gases contained in the valve pre-ignition chamber 1 to enter the combustion chamber 5, but it prevents the gases contained in said chamber 5 from entering the valve ignition pre-chamber 1.
• valve 13 When it is closed, the valve 13 turns the valve ignition prechamber 1 into a
• valve pre-ignition chamber 1 the easily flammable pilot charge 9 necessary without risk of mixing the latter with the main charge 30 which, on the contrary being hardly flammable, must be brought to a higher pressure and temperature to allow and promote it inflammation.
• cylinder head 3 and the active prechamber ignition insert 6 requires a tubular injection nozzle 54 of great length.
• the latter is incompatible with the technological and manufacturing constraints of compact and economical injectors usually used in automobiles.
• said great length does not pose any particular problem if recourse is had to the hydraulic cam injection system 100 according to the invention.
• Said temperature is imposed by the water which circulates in the cooling water chambers 41 of the cylinder head 3 of the internal combustion engine 2.
• the pressure of the injectable fluid 58 exceeded fifty bars, a part of the gasoline constituting the gas mixture AF would inevitably condense.
• tubular injection nozzle 54 injects the injectable fluid 58 into the valve ignition prechamber 1 to form the pilot charge 9 during the compression stroke of the internal combustion engine 2, while taking care that that the pressure in said prechamber 1 always remains lower than the pressure in combustion chamber 5.
• said system 100 makes it possible to produce a long and compact tubular injection nozzle 54, capable of injecting in less than forty degrees of shaft the pilot charge 9 required in the valve ignition prechamber 1, this despite an upstream pressure of the injectable fluid 58 limited to fifty bars due to its temperature limited to one hundred degrees Celsius.
• the booster pump 7 which supplies the hydraulic action conduit 78 with hydraulic fluid 60 via the booster non-return valve 8 is none other than the greasing pump of the internal combustion engine 2 while the hydraulic fluid tank 11 consists of the oil sump of said engine 2.
• the force produced by the return spring of the receiver piston 79 is expected to be substantially greater than the force produced by the pressure generated by the lubricating pump of the internal combustion engine 2 on the receiver piston. 62.
• injectable fluid supply pipe 66 is here arranged directly in the foundry of the cylinder head 3 while the injection cam 67 is driven by the camshaft of the cylinder head. internal combustion engine 2.
• rocker arm 80 bears on the cam housing 81 by means of a movable support roller 84 which can roll or slide on a displacement track 85 provided in the cam housing 81, said roller 84 cooperating with a tilting track 87 provided on the back of the rocker arm 80.
• FIGS. 1, 3, 5 , 6 and 12 it is noted that when the pawl roller 86 is in contact with the angular holding sector 16 and that the emitter piston 69 pushes on the rocker arm 80 via its axial action face 75 to press said rocker arm 80 on the track displacement 85 via the displaceable support roller 84, the tilting track 87 of said rocker arm 80 remains parallel to the displacement track 85 whatever the position of the displaceable support roller 84.
• the movable support roller 84 receives at each of its ends an orientation pinion 89, said pinions 89 being integral in rotation, while each said pinion 89 cooperates with a rack orientation 90 integral with the cam housing 81.
• the movable support roller 84 receives a worm wheel 91 which cooperates with a worm 92 whose axial position is fixed relative to the cam housing 81, said screw 92 being driven in rotation by the injector lift actuator 83 which, according to this non-limiting example, consists of an electric step-by-step motor 93.
• orientation 89 and that of the worm wheel 91 are identical, which does not exclude the possibility that they are different.
• the movable support roller 84 moves relative to the travel track 85 with which it cooperates which results in the displacement of the position of the movable bottom point 82 relative to the cam housing 81.
• the injection valve 50 is for example first kept closed by the receiving piston 62 due to the pressure which prevails in the tubular injection nozzle and, to a lesser extent. measurement, by the return spring of the receiving piston 79.
• This situation is illustrated in Figures 1 and 11, and results for example from any one of the angular positions of the injection cam 67 shown in Figures 1, 3, 5 or 6.
• FIG. 5 shows for its part that in order to adjust the lift height of the injection valve 50, the step-by-step electric motor 93 can bring the movable support roller 84 closer to or away from the emitter piston 69 by via the worm 92, this to modify the lever arm of the rocker arm 80 and therefore the displacement ratio between that of the emitter piston 69 and that of the receiver piston 62.
• the displacement ratio between the displacement of the emitter piston 69 and the effective lift of the injection valve 50 depends on the lever arm formed by the rocker arm 80, but also on the compressibility of the hydraulic fluid 60 contained in the emitting chamber 72, the receiving chamber 71 and the hydraulic action conduit 78.
• the force that must be applied by the rocker arm 80 on the axial action face 75 of the emitter piston 69 depends in particular on the pressure of the injectable fluid 58 which prevails in the tubular injection nozzle 54 and on the ratio between the section exposed to the pressure of the injectable fluid 58 by the axial face on the injectable fluid side 63 and the section exposed to said pressure by the tulip 52.
• the position of the step-by-step electric motor 93 is provided to vary as a function of requirements, and in particular as a function of the speed, of the load, and of the dilution of the main load 30 of the combustion engine. internal 2.
• dilution it is noted that the more the main charge 30 is diluted with fresh air or with recirculated exhaust gases, the more it is resistant to ignition, and the more energy it contains. in the pilot charge 9 must be large relative to that contained in the main charge 30.
• mapping of the ideal position of the step-by-step electric motor 93 taking into account the operating conditions of the internal combustion engine 2 is stored in the memory of a computer 48, corrected or not by algorithms taking into account contextual operating parameters such as temperature or
• tubular injection 54 must be drastically reduced, for example to five bars instead of fifty bars.
• hydraulic cam 100 is in no way limiting. Indeed, said system is capable of allowing the direct or indirect injection of natural gas, heavy fuel oil, diesel or gasoline into any internal combustion engine 2, whatever the principle.
• the invention is capable of allowing the injection of any gas and / or any liquid into any machine requiring such an injection, whether or not controlled by an injector lift actuator 83.

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• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• Fuel-Injection Apparatus (AREA)
• Valve Device For Special Equipments (AREA)

Applications Claiming Priority (4)

Publications (1)

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ID=69572061

Family Applications (1)

Country Status (8)

Family Cites Families (8)

• 2019
  • 2019-07-18 FR FR1908158A patent/FR3098858B1/fr not_active Expired - Fee Related
  • 2019-10-01 FR FR1910882A patent/FR3098857B1/fr not_active Expired - Fee Related
  • 2019-11-29 FR FR1913538A patent/FR3098868B1/fr not_active Expired - Fee Related
• 2020
  • 2020-07-16 EP EP20754324.0A patent/EP3999734A1/de not_active Withdrawn
  • 2020-07-16 JP JP2021576143A patent/JP2022541109A/ja active Pending
  • 2020-07-16 CA CA3144505A patent/CA3144505A1/en active Pending
  • 2020-07-16 AU AU2020315180A patent/AU2020315180A1/en not_active Abandoned
  • 2020-07-16 CN CN202080045699.7A patent/CN114051554A/zh active Pending
  • 2020-07-16 KR KR1020227002233A patent/KR20220034796A/ko not_active Withdrawn
  • 2020-07-16 WO PCT/FR2020/051283 patent/WO2021009466A1/fr not_active Ceased

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