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WO1992016737A1 - Pulverisateur automatique - Google Patents

Pulverisateur automatique Download PDF

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Publication number
WO1992016737A1
WO1992016737A1 PCT/DE1992/000213 DE9200213W WO9216737A1 WO 1992016737 A1 WO1992016737 A1 WO 1992016737A1 DE 9200213 W DE9200213 W DE 9200213W WO 9216737 A1 WO9216737 A1 WO 9216737A1
Authority
WO
WIPO (PCT)
Prior art keywords
fuel
needle part
exhaust gas
nozzle
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/DE1992/000213
Other languages
German (de)
English (en)
Inventor
Abdel Halim Saleh
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of WO1992016737A1 publication Critical patent/WO1992016737A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F02M67/00—Apparatus in which fuel-injection is effected by means of high-pressure gas, the gas carrying the fuel into working cylinders of the engine, e.g. air-injection type
    • F02M67/02—Apparatus in which fuel-injection is effected by means of high-pressure gas, the gas carrying the fuel into working cylinders of the engine, e.g. air-injection type the gas being compressed air, e.g. compressed in pumps
    • F02M67/04—Apparatus in which fuel-injection is effected by means of high-pressure gas, the gas carrying the fuel into working cylinders of the engine, e.g. air-injection type the gas being compressed air, e.g. compressed in pumps the air being extracted from working cylinders of the engine
    • 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
    • F02M53/00—Fuel-injection apparatus characterised by having heating, cooling or thermally-insulating means
    • F02M53/04—Injectors with heating, cooling, or thermally-insulating means
    • F02M53/06—Injectors with heating, cooling, or thermally-insulating means with fuel-heating means, e.g. for vaporising
    • 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
    • F02M67/00—Apparatus in which fuel-injection is effected by means of high-pressure gas, the gas carrying the fuel into working cylinders of the engine, e.g. air-injection type
    • F02M67/06—Apparatus in which fuel-injection is effected by means of high-pressure gas, the gas carrying the fuel into working cylinders of the engine, e.g. air-injection type the gas being other than air, e.g. steam, combustion gas

Definitions

  • Patent application WO 89/07193 describes an evaporator nozzle in which fuel is hermetically sealed over the duration of a cycle in an evaporator chamber so that it evaporates there before it is blown out into the combustion chamber at the known injection point in time in the next cycle by opening the blow-out holes .
  • the heat of evaporation required for this is extracted from an enveloping exhaust gas storage space. It was described there that the exhaust gas storage chamber is closed by its valves directed towards the combustion chamber as soon as the maximum pressure has been reached and after the start of combustion at the beginning of the working stroke. At this point, the piston is at top dead center.
  • the exhaust gas storage space valves are opened so that the old exhaust gases, after the required heat has been extracted, can flow back to the combustion chamber and thereby participate in the next combustion.
  • the exhaust gas storage chamber valves to the combustion chamber open until the maximum pressure in the combustion chamber is reached at the beginning of the next working stroke.
  • the exhaust gas storage space is first filled with fresh compressed air and then with a rich, burning mixture from the combustion chamber.
  • the exhaust gas storage space valves can be driven to the combustion chamber electrically or mechanically and that the blow-out holes and the injection holes can be closed by a needle provided with a double piston.
  • This needle was provided with spiral grooves, from which the fuel flows out to the evaporator chamber at high speed, causing the needle to rotate and exposing the steam outlet openings in the evaporator chamber.
  • the installation of a difficult rotation limit would be inevitable.
  • a nozzle is described which is controlled without an external drive and only by the fuel pump, the tasks described above being accomplished automatically and in a fixed relationship to the cycle.
  • the fuel is only delivered by the injection pump under high pressure into the evaporator nozzle at the end of the suction stroke and, as is the case in known injection pumps, does not end until after 0 to 20 degrees crankshaft angles after top dead center, as usual.
  • the nozzle needle Under the influence of the fuel pressure, the nozzle needle is set into a combined lifting and rotating movement, which leads to the valve movements described being fulfilled.
  • the exhaust gas storage valve is opened during the entire compression stroke. hold, the steam blow-out openings opened at the known injection point in time and after a few crankshaft angles later the fuel injection holes exposed, more or less all openings being closed again at top dead center.
  • Figure 1 is a detailed drawing of the new evaporator nozzle.
  • the nozzle consists of a nozzle housing 1, to which the exhaust gas storage space 2 is attached. Both parts 1 and 2 ⁇ close the nozzle body 3, the evaporator chamber 4 and a three-part needle 5-7 by screwing them together. Not shown is the known rest of the nozzle housing 1 together with the compression spring, which exerts pressure on the needle parts 5, 6 and 7 via a holder, and thereby keeps the fuel injection openings 8, the steam outlet openings 9 and the exhaust gas storage openings 10 closed.
  • the flat seal 11, the conical pressure surface 13 and the pressure surface 12 seal the nozzle interior 15, the evaporation space 16 and the exhaust gas storage space 17 against mutual leakage, also to the outside.
  • the evaporator chamber valve 18 would only be pressed against its compression spring 19 at a higher pressure of the gases in the exhaust gas storage space 17 than in the evaporation space 16, as a result of which a small proportion of the gases flow from the exhaust gas storage space 17 into the evaporation space 16.
  • the upper needle part 5 and the middle needle part 6 are coupled together by a driver pin 20.
  • the axial guide 21 in the nozzle body 3 allows the driving pin 20 together with the upper needle part 5 to be moved only in an axial stroke movement.
  • the position guide 22 in the central needle part 6 transmits this axial stroke movement of the driving pin 20 in the form of a rotary movement to the central needle part 6.
  • This rotary movement of the middle needle part 6 is about transmit a rectangular coupling directly to the lower needle part 7.
  • the needle parts 6 and 7 have channels or holes according to their function as rotary valves, which connect separate rooms.
  • the central needle part 6 also has fuel outflow bores 26 which expose the fuel injection holes 24 when the central needle part 6 is rotated. Only then can the liquid fuel flow from the fuel accumulation space 25 into the evaporation space 16 via the fuel outflow bores 26 and the fuel injection holes 24.
  • the lower needle part 7 has the steam outflow channels 27 and the exhaust gas flow channels 28.
  • the steam outflow channels 27 expose the steam outlet openings 9. Only then can fuel vapor flow out of the evaporation chamber 16 via the steam outlet channels 27 and the steam outlet openings 9 in the combustion chamber 30.
  • the exhaust gas flow channels 28 connect the exhaust gas flow channels 10 - in the evaporator chamber wall - to the exhaust gas storage space 17 and the exhaust gas flow channels 29 to the combustion chamber 30 together.
  • the old exhaust gases can be returned from the exhaust gas storage space 17 into the combustion space 30, or the compressed fresh air or the burning gas mixture can flow from the combustion space 30 into the exhaust gas storage space 17.
  • the number of channels 26, 27 and 28 on the circumference of the rotating needle parts 6 and 7 or the number of channels 24, 9, 10 and 29 in the fixed nozzle body 3 and evaporator chamber 4 is determined, among other things, by the desired number of cyclical processes which the needle parts 6 and 7 go through one revolution. This number " can be chosen, for example, between one and four cycles per revolution.
  • the timing and duration of the exposure of the channels 24, 9, 10 and 29 is determined, inter alia, by their position relative to the channels 26, 27 and 28 on the rotating needle parts 6 and 7 during the design.
  • the time sequence and duration in relation to engine operation is expressed below in the crankshaft angles, the crankshaft angles 0-180 representing the suction stroke, the crankshaft angles 180-360 the compression stroke and the crankshaft angles 360-520 the working stroke.
  • the desired opening sizes F of the channels 24, 9 and 10 with respect to the crankshaft angles KW at the opening times and durations desired in the patent specification WO 89/07193 are also plotted as crankshaft angles.
  • the exhaust gas flow channels 10 and 29 are connected through the exhaust gas flow channels 28 at the time when the piston in the cylinder passes through the crankshaft angles 185-370, and according to curve 2, the steam blowout openings 9 through the steam exhaust channels 27 become the corresponding crankshaft angles 330-365 exposed and according to curve 3, the fuel injection channels 24 through the fuel outflow bores 26 exposed to the corresponding crankshaft angles 340-370.
  • the channels 9, 10, 29, 27 and 28 are exposed four times per revolution of the needle part 7 and correspond to four circular processes.
  • the channels 9, 10, 29, 27 and 28 are only exposed twice per revolution of the needle part 7 and therefore correspond to two circular processes per revolution of the needle part 7.
  • the needle part 7 rotates in the direction of the arrow shown .
  • the rotary movement begins from the indicated point AI and ends in FIG. 3 after a quarter turn and in FIG. 4 after a half turn, the opening size, duration and time sequence indicated by the curves 1 and 2 in FIG. 2 being reproduced. This corresponds to a quarter turn in FIG. 3 or a half turn in FIG. 4, depending on the load, approximately 190 to 210 degrees crankshaft angle.
  • the channels 24 and 26 are shown after rolling up the circumference. They apply to the case in which the middle needle part 6 runs through four cycles per revolution and applies to the same nozzle shown in FIG. 4. From the beginning of the rotation in point AI, the opening 24 remains closed and is only closed at point A4 by the Fuel outflow channel 26 exposed. Only then will fuel injection begin.
  • the fuel outflow channel 26 is designed in shape and / or size so that the fuel injection at a predetermined crankshaft angle, for example at 370 degrees is ended. At this crankshaft angle, as shown below, the upper needle part 5 is in the lower part of its falling movement and at the end closes the fuel collection chamber 25.
  • the relative position of the rotating needle parts 6 and 7 to the fixed parts 3 and 4 determines the described sequence and duration of the opening of the channels 9, 10, 24, 26, 27, 28 and 29, and is dependent on the position of the upper needle part 5 in Its stroke path defines and results, as already described, from the interaction of the driving pin 20, the axial guide 21 and the shape of the position guide 22. This in turn is determined by the fuel pump, which has a fixed relationship to the camshaft or crankshaft angles.
  • the pressure of the fuel in the fuel accumulation chamber 25 rises above the opening pressure of the compression spring as a result of the compression effect of the fuel pump.
  • the upper needle part 5 is thereby lifted, and at the same time fuel flows from the fuel inlet channel 31 into the fuel accumulation chamber 25. This process continues until the upper needle part 5 has reached the end of its predetermined stroke.
  • the necessary contour shape of the position guide 22 is plotted on the middle needle part 6 against the circumferential angle W on the middle needle part 6, the starting point of the movement AI being set to the angle WA zero.
  • the needle parts 6 and 7 rotate by an angle W2 and at the end of the ascent of the upper needle part 5, ie to HM, the needle parts 6 and 7 rotate by the angle WM.
  • the curve passes through points A2, A3 and A4, at the corresponding angles W2, W3 and W4 the channels 29 and 10, 9 and 24 are exposed in turn, as already described.
  • the points AI, A2, A3 and A4 or WA, W2, W3 and W4 correspond to fixed crankshaft angles.
  • the angles W correspond to higher values of the crankshaft angles than was already shown.
  • This state corresponds approximately to the crankshaft angle difference in the length of the injection process between idling and full load.
  • the fuel injection from the channel 24 follows only due to the action of the compression spring of the injection nozzle.
  • the upper needle part 5 sinks into the middle needle part 6 and leads to further rotation of the needle parts 6 and 7 and finally when the angles WE2, WE3 and WE4 are reached in order to close the channels 24, 9 and 10.
  • the upper needle part 5 After the fuel injection openings 24 have been closed, the upper needle part 5 only sinks due to the leakage to the nozzle housing or back through the fuel inlet channels 31, which is only the case with some fuel pumps. In other fuel pump systems, the lowering of the upper needle part 5 becomes very slow and must therefore be derived through an extra leakage guide groove, which is only revealed after the fuel injection channels have been closed only until shortly before reaching WE or before zero. The further reaching of the height zero can then proceed slowly, so that the upper needle part 5 returns to its initial height zero in the next process at a crankshaft angle of 180 degrees at the end of the suction stroke. However, this zero height does not have to mean that the upper needle part 5 rests on the conical seat inside the middle needle part 6.
  • a further improvement can, according to FIG. 6, by enlarging the gap of the position guide 22 in the immediate vicinity of the reversal points, these are at the upper and lower ends of the stroke paths, as is indicated in FIG. 6 by the dashed line at zero and HM heights.
  • FIG. 7 shows another exemplary embodiment according to the invention based on the principle of the evaporator nozzle described above.
  • FIGS. 8, 10 and 11 show embodiments of an evaporator nozzle together with the nozzle assembly according to this design principle.
  • Figure 9 shows a section AA perpendicular to the axis of this nozzle assembly.
  • the nozzle assembly in FIGS. 8 to 11 consists of a nozzle assembly housing 1 to which the exhaust gas storage space 2 is attached. Both parts 1 and 2 close by screwing the nozzle body 3, the evaporator chamber 4 and a two-part needle 32-33.
  • a space or a gap 34 is provided, in which a gas cushion is formed by a connection with the evaporation space 16, which exerts pressure on the needle parts 32 and 33, and thereby holds the fuel injection openings 8, the steam discharge openings 9 and the exhaust gas flow openings 10 are closed.
  • the flat seal 11, the conical pressure surface 13 and the pressure surface 14 seal the nozzle interior 15, the evaporation space 16 and the exhaust gas storage space 17 against mutual leakage, also to the outside.
  • the evaporator chamber valve 18 would only be pressed against its compression spring 19 at a higher pressure of the gases in the exhaust gas storage space 17 than in the evaporation space 16, as a result of which a small proportion of the gases flow from the exhaust gas storage space 17 into the evaporation space 16.
  • an amount of liquid fuel metered precisely depending on the load flows from an injection pump (not shown) into the fuel supply channel
  • Needle portion 32 and causes upper needle portion 32 to rise from its seat 36, thereby allowing fuel to enter fuel storage space 25 and accumulate.
  • the upper needle part slides
  • the further supply of the liquid fuel in the nozzle leads to the fact that the fuel storage space 25 becomes larger and the needle parts 32, 33 continue to rotate.
  • the exposed exhaust gas storage opening 10 is, as is the case with the rotary slide valve, becoming larger and larger.
  • the pressure of the fresh charge in the cylinder increases during the compression stroke. A part of this fresh charge flows into the exhaust gas storage space 17.
  • the steam space 37 becomes smaller and smaller. Fuel vapor is therefore compressed from the vapor space 37 via the vapor escape holes 39 in the vaporization space 16 of the vaporization chamber 4, as a result of which the gas pressure in the vaporization chamber 4 increases far beyond the maximum achievable pressure in the combustion space 30.
  • the steam blow-out opening 9 is exposed by the lower needle part 33 at a certain crankshaft angle, as a result of which the highly compressed fuel vapor suddenly flows out of the evaporation space 16 in the combustion chamber 30.
  • the fuel injection opening 24 is exposed, as a result of which liquid fuel is injected into the evaporation space 16 from the fuel storage space 25.
  • the upper needle part 32 then stops until the fuel injection or the fuel supply has ended, in order to immediately turn back when the fuel pressure, which in turn is operated by the injection pump, collapses, and in turn the remaining liquid fuel from the fuel storage space 25 in pump the injection pump back.
  • the pumping back is effected by the highly compressed gas in the vapor space 37 or in the evaporation space 16, which in turn is expanded during the pumping back, and a part of the exhaust gases in the evaporation space 16 is sucked off via the exhaust gas recirculation valve 18.
  • the steam begins Combustion of the gases in the cylinder.
  • the pressure of the combustion gas increases and reaches its maximum value shortly after the compression stroke.
  • a burning gas mixture flows into the exhaust gas storage space 17.
  • the flow of the burning gases continues until the pressure in the exhaust gas storage space has reached the pressure in the combustion chamber.
  • this time is shortly after the gas pressure in the cylinder has reached its maximum value described above.
  • the liquid fuel supply has already ended and the needle parts 32 and 33, as mentioned above, turn back.
  • the turning back of the needle parts 32 and 33 proceeds quickly and closes the fuel injection openings 24, the steam outlet openings 9 and the exhaust gas storage opening 10 one after the other and therefore follows the curves in FIG. 2.
  • the seat of the lower needle part 40 can take various forms, based on the principle of a slide valve. Preferred exemplary embodiments of this are shown in FIGS. 8, 10 and 11.
  • the exhaust gas recirculation valve 18 can, as shown in FIGS. 2, 7 and 10, be installed in the wall of the evaporator chamber 4 and thus closes the evaporation space 16 directly with the exhaust gas storage space 17 or, as shown in FIG. 8, with an interior 41 in the lower needle part 33, which is connected to the exhaust gas storage space 17 via a channel 42. In the latter case, the lower needle part 33 is also heated by the exhaust gases in the interior 41.
  • the timing of the filling and emptying of the interior 41 depends on the relative position of the channel 42 to the exhaust gas storage opening 10, and can be designed so that the interior 41 is only open or closed Abga ⁇ peicherraum 17 is connected. It should be noted that exhaust gas recirculation and needle heating above an interior are not always necessary. Dispensing with their installation, as shown in Figure 11, makes a significant contribution to simplifying the structure of the nozzle stick.
  • the evaporator nozzle assembly as shown in FIGS. 8 to 11, can be used as an additive in known systems after removal of the housing part 1.
  • the use of this additive as a replacement for the known nozzle part in a pump nozzle system is preferred here and therefore results in a novel evaporator pump nozzle.
  • this new type of evaporator pump nozzle requires less height, significantly lower fuel pressures and lower pumping capacities, it allows greater play between the components and therefore less friction.
  • FIG. 12 an embodiment can be represented in FIG. 12 by a combination of the embodiments in FIGS. 1 and 7.
  • the upper needle part 5 can therefore be regarded as a part of the nozzle block housing 1.
  • the fuel supply channel 31 will pierce the upper needle part 5, and the injection will only begin after a certain elevation of the middle needle part 6 relative to its seat 36, the middle needle part 6 being displaced downwards in a spiral movement consisting of a lifting and rotating movement , and thereby releases the connection of the fuel injection openings 24 to the fuel collection chamber 25.
  • the course of the position guide 22 in the upper needle part 5 can be built as a mirror image of that in FIG. 1 or 7. Therefore, the unavoidable pressure relief, of the steam in the evaporation space 16 of the embodiment in FIG. 7, is used here for the desired compression of the steam in the evaporation space 16 when blowing out. Similar to the case in FIG. 7, the axial guide 21 is not required here.
  • the driver pin 20 is fastened in the middle needle part 6.
  • FIG. 13 shows a preferred embodiment of the evaporator nozzle assembly. It differs only slightly from the embodiment in FIG. 12.
  • the upper needle part 5 ends directly in the lower needle part 7 and is therefore similar to the lower needle part 33 in FIG. 11 and will only rotate.
  • the middle needle part 6 of the axial guide 21 in the evaporator chamber wall and over that in the needle part 6th attached driver pin 20 only allows a downward and backward lifting movement.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

Dans un dispositif pour l'introduction notamment de carburant à auto-allumage dans la chambre de combustion d'un moteur à combustion interne à un ou plusieurs cylindres au moyen d'un injecteur ou pulvérisateur pour du carburant dosé, constitué du corps de l'injecteur/pulvérisateur (1), du collecteur de gaz d'échappement (2), du corps d'injecteur/pulvérisateur (3), de la chambre de pulvérisation (4) et d'une aiguille d'injecteur/pulvérisateur, le mouvement de levée de la partie supérieure de l'aiguille (5, 23) de son siège provoqué par l'arrivée du carburant doit se traduire en un mouvement de rotation prédéterminé de la partie centrale (6) et inférieure (7, 33) de l'aiguille par l'intermédiaire d'un trou de guidage (22).
PCT/DE1992/000213 1991-03-15 1992-03-13 Pulverisateur automatique Ceased WO1992016737A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DEP4108526.4 1991-03-15
DE4108526 1991-03-15
DE19914141852 DE4141852A1 (de) 1991-03-15 1991-12-18 Selbstaetige verdampferduese
DEP4141852.2 1991-12-18

Publications (1)

Publication Number Publication Date
WO1992016737A1 true WO1992016737A1 (fr) 1992-10-01

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ID=25901918

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1992/000213 Ceased WO1992016737A1 (fr) 1991-03-15 1992-03-13 Pulverisateur automatique

Country Status (2)

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DE (1) DE4141852A1 (fr)
WO (1) WO1992016737A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2003900748A0 (en) * 2003-02-13 2003-03-06 Vaporate Pty Ltd Fuel delivery system

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2229552A (en) * 1937-08-26 1941-01-21 Samuel P Cowardin Apparatus for injecting fuel into internal combustion engines
WO1989007193A1 (fr) * 1988-01-29 1989-08-10 Abdel Halim Saleh Procede pour actionner un moteur a combustion interne mono ou multicylindre

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2229552A (en) * 1937-08-26 1941-01-21 Samuel P Cowardin Apparatus for injecting fuel into internal combustion engines
WO1989007193A1 (fr) * 1988-01-29 1989-08-10 Abdel Halim Saleh Procede pour actionner un moteur a combustion interne mono ou multicylindre

Also Published As

Publication number Publication date
DE4141852A1 (de) 1992-09-17

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