EP0152321B1 - Anlage zur Kontrolle für das Öffnen und Schliessen der Brennkammer einer Brennkraftmaschine - Google Patents

Anlage zur Kontrolle für das Öffnen und Schliessen der Brennkammer einer Brennkraftmaschine Download PDF

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Publication number
EP0152321B1
EP0152321B1 EP19850400107 EP85400107A EP0152321B1 EP 0152321 B1 EP0152321 B1 EP 0152321B1 EP 19850400107 EP19850400107 EP 19850400107 EP 85400107 A EP85400107 A EP 85400107A EP 0152321 B1 EP0152321 B1 EP 0152321B1
Authority
EP
European Patent Office
Prior art keywords
inlet
passage
combustion chamber
chamber
combustion
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.)
Expired
Application number
EP19850400107
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English (en)
French (fr)
Other versions
EP0152321A1 (de
Inventor
Jean-Claude Fayard
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.)
Elf Antar France
Original Assignee
Elf France SA
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
Priority claimed from FR8410675A external-priority patent/FR2549490A1/fr
Priority claimed from FR8500637A external-priority patent/FR2576060B2/fr
Application filed by Elf France SA filed Critical Elf France SA
Priority to AT85400107T priority Critical patent/ATE30456T1/de
Publication of EP0152321A1 publication Critical patent/EP0152321A1/de
Application granted granted Critical
Publication of EP0152321B1 publication Critical patent/EP0152321B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/02—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves
    • F01L7/021—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves with one rotary valve
    • F01L7/022—Cylindrical valves having one recess communicating successively with aligned inlet and exhaust ports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/16—Sealing or packing arrangements specially therefor
    • 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
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into 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
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • 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
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four

Definitions

  • the present invention applies to a device for controlling the circulation of gases to and from a combustion chamber of an internal combustion engine, constituted by a rotary plug or rotor comprising at least one internal channel or a lateral cut defining passages of 'respective exhaust or intake transverse flow, a passage directly connected to the combustion chamber, the plug being contained in a transverse bore into which opens the orifice of said passage arranged in a sealing ring which is housed in a bore, in which it slides, the sealing ring being applied to the rotor by a continuous contact surface around the orifice of the passage under the effect of the pressure prevailing in the combustion chamber being surrounded by one or several sealing members such as segments, and being provided with means for injecting oil on the plug.
  • the plug is contained in a transverse bore into which opens the orifice connected directly to the combustion chamber and the intake and / or exhaust orifices connected respectively to an exhaust manifold.
  • the passage connected to the combustion chamber is arranged in a sealing ring housed in an applied bore, on the plug by a continuous sealing surface around the orifice connected directly to the combustion chamber, under the effect of the pressure prevailing in the combustion chamber, and surrounded by one or more, sealing members such as segments, this ring being able to slide in the bore and its stroke being limited, on one side, by the plug and, on the other side, by a retaining shoulder.
  • Such combustion engines appear capable of delivering mass powers much higher than known and proven solutions, in particular for small displacement engines, due to the absence of distribution parts subjected to an alternating movement generating a beat limit frequency.
  • the most decisive advantage of this type of distribution lies in the possibility of having exhaust and intake ducts twice the diameter of a conventional valve system, which allows for better filling. and therefore a higher specific power.
  • US-A-4,114,639 describes a rotary valve used for controlling the circulation of gases to and from a combustion chamber of an internal combustion engine and into which the lubricant is supplied using porous plugs between the member of the rotating valve and the inner surface of the valve body supporting this rotating member.
  • the seal between the insert forming an annular seal and the rotating member forming the supply and exhaust distributor cannot be maintained over time. There is in fact no means of placing the insert on the member other than that due to the oil pressure or the combustion pressure of the chamber.
  • This known system has the drawback, in the event of wear on contact between the insert and the rotating member, an exhaust gas leak is established towards the oil supply line and a discharge of lubricating oil, followed by seizure of the rotating contact.
  • One of the aims of the present invention is precisely to overcome these defects of combustion engines with rotary distribution in order to allow the large passage sections offered by this type of their distribution to be used without risking rapid wear and consumption of exaggerated fuel.
  • the sealing ring is crossed at least at its periphery by a pressurized oil circuit heading towards the oil return and capable of ensuring cooling.
  • this ring and the injection means are connected to said oil circuit, pass axially through at least part of the annular section of the ring and open into a continuous annular distribution groove which is formed inside the continuous contact surface established on a strip of small width along the general line of intersection of two cylinders and which opens on the interface existing between this contact surface and the external surface of the rotor.
  • the means for injecting the fluid consist, on the one hand, of an annular oil intake and circulation chamber, delimited between the periphery of the sealing ring and its bore and axially limited at each end by a seal interposed between the outer surface of the sealing ring and the bore and, on the other hand, by at least one supply passage having an outlet opening opening into said interface between the surface continuous sealing and the outer surface of the plug and in that at least one gun sealing segment is interposed between on the one hand the sealing ring and its bore and on the other hand said seal located on the side of the combustion.
  • the annular inlet chamber is traversed by a large flow of pressurized oil directing through an outlet pipe towards another member to be lubricated or the discharge.
  • an end part of at least one supply member for one of the combustion elements crosses in a leaktight manner the cross section of the sealing ring to open into the passage which is connected to the combustion chamber, and in that the adjacent part of said end part is housed with an annular clearance in a supply passage towards the outside of said combustion element, said supply passage being connected to the annular fluid intake chamber.
  • the passage giving rise to the annular clearance is traversed by a flow of the fluid brought to the annular fluid admission chamber.
  • the passage giving rise to the annular clearance is extended towards the outside by an enlarged annular chamber, which is closed by a seal.
  • elastic ring interposed between the supply member and the inner wall of said chamber and delimiting a cooling chamber traversed by said fluid flow.
  • the sealing ring is, on the one hand, made of a soft material having good rubbing qualities with the surface of the plug, for example plastic, and, on the other hand, permanently pushed back on the surface of the plug under a substantially constant pressure by a spring.
  • scraper means lubricating fluid injected into the interface are arranged around the intake orifice connecting the rotor to the intake of the mixture of combustion air and engine fuel, these scraper means being constituted by a sealing ring intake disposed at the periphery of said intake port, which comes into continuous support on the outer surface of the plug and which is capable of isolating the interior of the intake port from the interface between the plug and its bore to limit the entrainment of oil and liquid fuel simultaneously on the surface of the rotating plug.
  • the sealing ring is, on the one hand, made of a soft material having good rubbing qualities with the surface of the plug, for example plastic, and, on the other hand part, permanently pushed back on the surface of the plug under a substantially constant pressure by a spring.
  • the plug has two separate inlet and outlet passages respectively which are capable of successively opening both by rotation of the plug, on the side of the combustion chamber, on the sealing ring and, on the side opposite to the combustion chamber, on outlet orifices which are each offset on the axis of the plug relative to the sealing ring, so as to reduce the entrainment of the fuel to the surface of the plug and the fuel entrained at the intake in the intake passage formed inside the plug.
  • the separate intake or exhaust passages of two neighboring combustion chambers are provided in the plug, opening onto an orifice for communication with the intake or the exhaust which is common to the two adjacent combustion chambers, so as to reduce the number of openings to be provided on the outside face of the plug.
  • the intake circuit of the combustion chamber includes means for removing fuel from the air drawn into the combustion chamber. combustion before the end of admission.
  • the abovementioned suppression means consist of stopping the injection of fuel clearly before the end of the suction phase.
  • the abovementioned suppression means are then preferably constituted by at least one auxiliary passage of air rich in fuel such as an emulsion, formed in the plug and cylinder head of the combustion chamber and the auxiliary passage leads to the interface between the plug and its bore at a point such that it is closed by the rotation of the plug before the main opening (s) (s) of admission not the self.
  • the suppression means are constituted by stopping the injection of fuel clearly before the end of the suction phase.
  • the suppression means are constituted by at least one auxiliary passage of air rich in fuel, formed in the plug and the cylinder head of the combustion chamber and which opens onto the interface between the rotor and its bore in an orifice which is closed off by the rotation of the rotor before the main opening (s) of inlet (s) are self-contained.
  • the passage giving rise to the annular clearance is extended towards the outside by an enlarged annular chamber, said annular chamber being closed by an elastic annular seal which is interposed between the inlet and the inner wall of said chamber and which delimits a cooling chamber through which the lubricating and cooling fluid flows brought in by the injection means.
  • This enlarged part allows a tool to access the feed member.
  • US-A-4,114,639 describes a rotary valve used for controlling the circulation of gases to and from a combustion chamber of an internal combustion engine and into which the lubricant is supplied using porous plugs between the member of rotating valve and the lower surface of the valve body supporting this rotating member.
  • a rotary plug 1 for distributing the exhaust of a combustion chamber 2 of a heat engine is shown at the moment when its internal exhaust channel 3 is opened wide on the combustion chamber 2.
  • the plug 1 turns, continuously and synchronously with the rotation of the engine, in a bore 4 and the exhaust channel 3 is connected to the combustion chamber 2 by a passage 5 of relatively large dimension formed in a ring seal 6 which can slide freely in a bore 7 with an axis substantially parallel to that of the engine cylinder (not shown) or substantially perpendicular to the axis of rotation of the plug 1, so as to ensure good bearing of the surface of contact of the ring 6 on the outer surface 8 of the plug 1.
  • the contact surface 22 between the ring 6 and the plug 1 is established on a strip of small width along the general line of intersection of two cylinders (the exterior surfaces of the wood bucket 1 and ring 6 of different diameters and substantially perpendicular and concurrent axes.
  • the sealing ring 6 which moves with gentle friction in its bore 7 is applied to the outer surface of plug 1 by the single pressure prevailing in combustion chamber 2 and acting on its annular section, increased if necessary by the thrust of a spring with low reaction force such as a washer elastic.
  • this thrust spring (not shown) of the ring 6 on the plug 1 is not essential if there is only a slight clearance or interface i between the end 9 of the ring 6 of the side of the combustion chamber 2 and a retaining shoulder 10 formed at the end of the bore 7 receiving the ring 6.
  • the temperature being relatively high in the interface i because of the proximity of the chamber 2 combustion, the holding over time of a spring member is very random.
  • a gun sealing segment 11 is disposed in a known manner in this interface j and is worn by a groove 12 preferably made in the ring 6. The segment 11 also prevents overheating of the interface j in the direction of the plug 1 and the formation in this interface of deposits which would end up blocking the ring 6 in its bore 7 .
  • the sealing ring 6 is provided with means for injecting a lubricating and cooling fluid, preferably engine lubricating oil pressurized by the engine oil pump, into the interface e between the continuous sealing surface 22 (along the general line of orthogonal intersection of two cylinders of different diameters) around the orifice 3 formed in the plug 1 and the external surface 8 of the plug 1.
  • a lubricating and cooling fluid preferably engine lubricating oil pressurized by the engine oil pump
  • the fluid injection means comprise a line 13 for supplying pressurized oil usually connected to the engine lubrication pump and leading to an annular distribution chamber 14, delimited in the interface j between the periphery of the ring 6 and its bore 7 for example using a cir groove cular 15 formed at the periphery of the sealing ring 6.
  • the chamber 14 can be traversed by a large flow of oil under pressure moving towards another member to be lubricated or discharge via an outlet pipe 16.
  • the chamber 14 is delimited in the interface j by two annular seals 17 and 18 disposed respectively on the side of the combustion chamber 2 and on the side of the plug 1.
  • the annular seals 17 and 18 are preferably made of a resistant elastomeric material for seal housed by elasticity in annular grooves formed on the outer surface of the ring 6 because the gun segment 11 1 and the circulation of oil protect against excessive temperature.
  • the oil distribution chamber 14 is connected to the interface e between the sealing surface of the ring 3 and the external surface 8 of the plug 1 by supply passages 19 made, preferably, by a longitudinal bore. in the thickness of the ring, connected to a transverse bore 20 from the bottom of the circular groove 15.
  • the supply passages 19 can lead to the interface e directly by an outlet chamfer or else in an annular groove continuous distribution 21 formed inside the contact or sealing surface 22 of the ring 6, this in order to better distribute the oil in the interface e.
  • the channel 6 formed inside the rotary valve 1 can be a channel for the admission of fresh gases (normally pressurized air or at atmospheric pressure) fueled or not, or else an exhaust channel combustion gases as described above and that the channel 3 can be replaced, as will be seen hereinafter, by a lateral notch successively filling, during the rotation of the plug, the functions of intake and exhaust passage.
  • tion 2 during the compression and gas combustion phases strongly applies the sealing surface 22 to the outer surface 8 of the plug 1 and reduces the thickness of this oil blade to a minimum value just sufficient to ensure a film of oil between the surface of the plug 1 and the sealing surface 22.
  • the friction hysteresis of the gun segment 11 of the ring 6 on the plug 1 maintains a significant residual application force of the ring 6 on the plug 1.
  • This residual force limits oil leaks between the sealing surface 22 and the surface 8 of the plug at a flow rate just sufficient to ensure a continuous film of oil between the surface 8 of the plug 1 and its guide bore 4.
  • the wear of the sealing surface 22 of the ring 6 is reduced to a minimum value and the risks of seizure at high speed of the ring 6 on the plug 1 are deleted.
  • the temperature of the surface of the plug 1 (moreover generally cooled internally by a longitudinal circulation of water) is considerably reduced and the seal between the plug and its bore 4 is ensured by an oil wedge.
  • the circulation in diversion of the oil between the supply pipe 13 and the outlet pipe 16 ensures an energetic cooling of the sealing ring 6 which could thus in certain application cases be made of a relatively soft material and good rubbing quality such as high strength molded plastic.
  • the sealing ring 6 as well as the plug 1 can be produced, preferably, in the different friction couples usually used in engines such as: cast iron / chrome, cast iron / cast iron, etc., but also in new composite materials , ceramics or other new products.
  • a calibrated orifice (not shown) can be placed on the inlet pipe 13 or on the supply passages 19 in order to limit the flow of oil escaping from the interface e when the pressure drop caused by the passages is insufficient to limit the oil leakage rate.
  • the sealing ring 6 can be made of porous sintered metal with a sealing plating on the surfaces which should not give rise to an exudation of oil, or else as shown in FIG. 2, an annular ring or cartridge 23 made of porous sintered metal, such as bronze, is introduced or molded in a blind housing 19a formed longitudinally in the sealing ring 6.
  • This porous ring 23 is connected by at least one lateral passage 20 to the oil pressure distribution chamber 14.
  • the porous ring 23 thus functions as a pressure drop and oil distribution member in the interface e and as a good-quality rubbing member reducing the friction between the ring 6 and the rotary plug 1. This arrangement which appears suitable for cases where the speed of rotation of the plug 1 is moderate and where vigorous cooling of the sealing ring 6 is not required, reduces oil losses and is generally more economical to implement than the solution shown in fig. 1.
  • FIGS. 3a to 3c schematically represent the most characteristic positions of a plug 1 provided, not with an internal channel, but with a notch 24 intended to ensure the distribution (suction and exhaust) of a combustion chamber 2 of an internal combustion engine operating according to the four-stroke cycle.
  • the notch 24 connects the combustion chamber 2 of the engine (via a sealing ring of the type described in FIGS. 1 and 2 and not shown) to a suction pipe 25 provided with introduction means fuel such as a carburetor or injector, if the engine is operated with a positive ignition.
  • introduction means fuel such as a carburetor or injector
  • the notch 24 of the plug 1 delimits with the guide bore 4 valve 1 a passage chamber 27 of a significant volume and which is then isolated from the intake and exhaust.
  • the chamber 27 was filled during the intake phase with air relatively rich in fuel since it was sucked in after the walls of the suction pipe were saturated with liquid fuel.
  • the air rich in fuel contained in the passage chamber 27 is completely discharged to the exhaust 26, in particular as a result of the arrival of the puff of exhaust gas at the time of setting up communications (not shown) of the combustion chamber 2 with the chamber 27 when the edge 28 of the notch 24 opens onto the passage 5 connected to the combustion chamber 2.
  • FIG. 4 shows, on a larger scale, a solution to reduce fuel and oil losses. Elements identical to those in FIGS. 1 to 3c are given the same reference numbers.
  • oil scraper means are arranged around the air intake orifice on the plug 1.
  • the scraper means are constituted by an intake sealing ring 29 permanently applied to the surface 8 of the plug 1 by a spring 30.
  • the fuel introduction means constituted here by a petrol injector 31 are adjusted so that the injection is cut off well before the end of the combustion air suction phase.
  • the sealing ring 29 housed in the cooled cylinder head 32 of the engine and through which the fresh intake gases pass is neither subjected to high temperatures nor to significant pressure differences (the overpressures and depressions are less than 1 bar) and as a result, it can be made of a good rubbing plastic material such as Teflon.
  • the operation of the embodiment shown in FIG. 4 is described below.
  • the plug 1 rotates in synchronism with the motor and receives from the supply passages 19 and the distribution groove 21 an oil film which is driven on its surface 8.
  • the oil film formed in the interface between the plug and the bore 4 is stopped by the sealing ring 29 substantially of the same width as the main sealing ring 6.
  • the injection of fuel by the injector 31 begins as soon as the edge 28 of the notch 24 leads to the inner passage 33 of the suction ring 29 and stops well before the other edge 34 of the notch 24 reaches the right edge 35 of the passage 5 formed inside the ring 6 and does not cut off the intake.
  • FIGS. 5 and 6 Another embodiment of the device for controlling the circulation of gases to and from an engine combustion chamber is shown in FIGS. 5 and 6 in which the elements and members identical to those of the preceding figures have the same reference numbers.
  • the plug 1 has two separate inlet and outlet passages 36 and 37 respectively. Each of these two passages successively opens by rotation of the plug 1 on the side of the combustion chamber 2 on the ring d seal 6 and, on the opposite side, on orifices which are laterally offset with respect to the seal ring 6.
  • the intake passage 36 opens from one side of the cylinder head onto the suction pipe 25 surrounded by its suction seal ring 29.
  • the exhaust passage 37 opens onto the passage 5 inside the ring 6 and onto the exhaust pipe 26 offset along the axis of the plug 1 with respect to the sealing ring 6.
  • the two intake passages 36 and 36a of two combustion chambers adjacent to an engine lead to a common orifice 38 for communication with the intake pipe 25 common to the two cylinders.
  • This arrangement which also applies to the exhaust ducts and orifices, makes it possible to reduce the number of outlets to be provided in the plug 1 and the cylinder head 32 which constitute as many zones of weakening of the mechanical resistance of these highly stressed members on the mechanical and thermal plans.
  • the intake channel 25 shown in cross section in FIG. 8 and in longitudinal section in FIG. 9, comprises two auxiliary passages 39 and 40 for supplying a fuel-rich mixture such as an air-petrol emulsion obtained by injecting petrol using an injector 31 (conduit 39 in FIG. 9 ) or by an emulsion carburetor 41 (line 40 in fig. 9).
  • a fuel-rich mixture such as an air-petrol emulsion obtained by injecting petrol using an injector 31 (conduit 39 in FIG. 9 ) or by an emulsion carburetor 41 (line 40 in fig. 9).
  • a single auxiliary duct 39 is sufficient to ensure the correct metering of the fuel.
  • the auxiliary conduits 39 and 40 are closed before the enlarged part 25a of the conduit 25 is so and the air sucked in at the end d suction on the large section 25a does not contain fuel and sweeps the passage chamber 27 delimited by the notch 24 to deplete it of almost all the liquid fuel deposited on its walls, so that when this passage chamber is through which the exhaust gases pass, these entrain only a minute quantity of fuel thus unused towards the exhaust pipe 26.
  • FIGS 10 and 11 illustrate the mounting of a supply member connecting the combustion chamber 2 to the outside such as a spark plug 42 used when the heat engine is an internal combustion engine with controlled ignition.
  • a spark plug 42 used when the heat engine is an internal combustion engine with controlled ignition.
  • the spark plug 42 may be replaced by a fuel injector or a glow plug.
  • the spark plug 42 is screwed into a thread 43 formed through a thin wall area 44 of the cylinder head 32 of the engine, so that its electrodes 45 (connected to ground) and 46 protrude slightly from the interior of the combustion chamber 2.
  • most of the combustion chamber in the vicinity of the top dead center of the piston (not shown) is constituted by the passage 5 of relatively large dimension formed in the sealing ring 6.
  • the spark plug 42 is placed in the position shown in FIG. 10, the fuel mixture is ignited relatively poorly because it does not start in a central position relative to the main volume of the combustion chamber at top dead center.
  • Fig. 11 illustrates in section an arrangement of the spark plug 42 (or where appropriate of a fuel injector or of a heating plug) which overcomes the drawbacks of the mounting solution shown in FIG. 10.
  • the sealing ring 6 comprises between two supply passages 19 a thread 43 for receiving the end portion or base 47 of the spark plug 42 which, in the sealed mounting position through this thread crossing the cross section of the ring 6, projects by its electrodes 45 and 46 inside the passage 5 in the vicinity of the wall but substantially at the center of the main combustion chamber formed by this passage 5.
  • the spark plug rod 48 which constitutes the part adjacent to the base 47 crosses with play a relatively narrow passage 49 formed through the wall of the cylinder head 32.
  • the passage 49 is connected to the outside by a bore 50 of larger diameter forming a annular chamber 51 into which the outlet pipe 16 opens.
  • an elastic annular seal 53 is interposed between the wall of the bore 50 and the cylindrical insulator 52 of the outlet terminal 54 of the candle 42.
  • the position of the ring 6, relative to the rotary plug 1, is likely to vary in service as a result of the expansion of the ring 6, variable axial and radial pressure forces on this ring 6 and especially wear progressive sealing surface 22 of this ring in rubbing contact with the surface 8 of the rotor 1, this wear varying lejeu i.
  • the instantaneous (at each explosion) and progressive movements of the ring 6 do not disturb the sealing of the chamber 51 and the position of the spark plug in the cylinder head 32 thanks, on the one hand, to the play in the passage 49 and avoiding any contact between the cylinder head 32 and the spark plug rod 48 and, on the other hand, the elasticity of the annular seal 53 preferably produced in one elastomeric material.
  • the fuel injector could advantageously be cooled while the glow plug should not be or should be as little as possible, which is achievable by placing it in an insulating envelope.
  • the mounting device assembly system shown in FIG. 11 carries out a mechanical and vibratory decoupling between, on the one hand the sealing ring 6 which delimits most of the combustion chamber at the top dead center of the piston and, on the other hand, the cylinder head 32. Thanks to the properties damping the elastomer of the seal 53 and the annular seals 17 and 18, not only the possible vibrations of the ring 6 can not be transmitted to the cylinder head and vice versa but, in addition, these vibrations are damped at their frequency critical by the large mass of elastomer of the joint 53.
  • the spark plug 42 is mounted on the thread 43 of the ring 6 outside the refrigerant circuit passing through the annular chamber 14.
  • the chamber 14 is, by example, placed near the upper end (in the drawing) of the ring 6 and in the vicinity of the interface e, the spark plug base 47 being placed either in the vicinity of the middle of the height of the ring 6 , which is closer to combustion chamber 2.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Claims (13)

1. Vorrichtung zur Steuerung der Gasströmung in die bzw. aus der Brennkammer (2) einer Brennkraftmaschine, bestehend aus einem Ventilhahn bzw. Rotor (1) mit wenigstens einem inneren Kanal (3) oder einer seitlichen Einkerbung (24) zwecks Bildung je eines Querströmungswegs für den Auspuff oder den Einlass, wobei ein Durchlass (5) unmittelbar mit der Brennkammer (2) verbunden ist und der Ventilhahn (1) in einer Querbohrung (4) angeordnet ist, in welche die Öffnung des Durchlasses (5) einmündet, der in einem in einer Bohrung (7) gleitbar angeordneten Dichtungsring (6) gebildet ist, der mit einer durchgehenden Berührungsfläche (22) an dem Rotor unter Einwirkung des in der Brennkammer (2) herrschenden Druckes anliegt und von einem oder mehreren Dichtungsorganen (11) wie Dichtungssegmenten umgeben, sowie mit Mitteln (29, 23) zum Einspritzen von Öl auf den Ventilhahn (1) versehen ist, dadurch gekennzeichnet, dass der Dichtungsring (6) wenigstens an seinem Umfang von einem Druckölkreislauf (13, 14, 16) durchquert wird, der in Richtung des Ölrücklaufs verläuft und den Dichtungsring (6) kühlt, und dass die Einspritzmittel (19, 23), die an den ÖIkreislauf (13, 14, 16) angeschlossen sind axial wenigstens einen Teil des ringförmigen Querschnitts des Ringes (6) durchqueren und in eine durchgehende ringförmige Verteilernut (21) münden, die innerhalb der durchgehenden, in einem schmalen Bereich längs der Hauptschnittlinie zweier Zylinder ausgebildeten Berührungsfläche (22) angeordnet ist und an der Zwischenfläche (e) zwischen dieser Berührungsfläche (22) und der Aussenfläche (8) des Rotors (1) mündet.
2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass die Öleinspritzmittel einerseits eine ringförmige Öleinlass- und Umlaufkammer (14) umfassen, die durch den Umfang des Dichtungsrings (6) und durch dessen Bohrung (7), sowie an jedem ihrer Enden axial durch je einen zwischen der Aussenfläche des Dichtungsrings und der Bohrung (7) angeordnete Ringdichtung (17, 18) begrenzt wird, und andererseits wenigstens einen Zuführungsdurchlass (19) aufweisen, dessen Auslassöffnung in der Zwischenfläche (e) zwischen der durchgehenden Dichtungsfläche (22) und der Aussenfläche (8) des Ventilhahns (1) mündet, und dass wenigstens ein Branddichtungssegment (11) zwischen dem Dichtungsring (6) und seiner Bohrung (7) einerseits und derjenigen Ringdichtung (17) andererseits angeordnet ist, die brennkammerseitig (2) liegt.
3. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass die ringförmige Einlasskammer (14) von einer erheblichen Ölmenge unter Druck durchströmt wird, welche durch eine Ausgangsleitung (16) zu einem anderen zu schmierenden Organ oder zum Abfluss geleitet wird.
4. Vorrichtung nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass ein Endteil (45, 46, 47) wenigstens eines der Einlassorgane eines der Verbrennungselemente, beispielsweise einer Zündkerze (42) bei einen Motor mit gesteuerter Zündung oder ein Injektor bzw. eine Glühkerze bei einem Dieselmotor durch den Querschnitt des Dichtungsringes (6) dicht hindurchgeführt ist, um in den Durchlass (5) zu münden, der mit der Brennkammer verbunden ist, und dass der diesem Endteil benachbarte Teil (48) mit Umfangsspiel in einem nach aussen führenden Zuführungsdurchlass (49) für das genannte Verbrennungselement angeordnet ist, wobei dieser Zuführungsdurchlass (49) mit der ringförmigen Mediumeinlasskammer (14) verbunden ist.
5. Vorrichtung nach Anspruch 4, dadurch gekennzeichnet, dass der das Umfangsspiel bestimmende Durchlass (49) von einer in die Mediumeinlasskammer (14) eingelassenen Mediumströmung durchströmt wird.
6. Vorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass der das Umfangsspiel bestimmende Durchlass (49) nach aussen durch eine erweiterte ringförmige Kammer (52) fortgesetzt ist, die durch einen zwischen dem Einlassorgan (42) und der Innenwandung (50) dieser Kammer (51) angeordneten elastischen Dichtungsring (53) verschlossen ist, der eine Kühlkammer (14, 49,51) begrenzt, welche von der Mediumströmung durchflossen wird.
7. Vorrichtung nach einem der Ansprüche 1 bis 6, verwendet bei einer Wärmekraftmaschine, und bei welcher der Rotor (1) gleichzeitig zur Steuerung des Auspuffs der Kraftmachine und des Brennstoff- und Luftgemischeinlasses in die Brennkammer dient, dadurch gekennzeichnet, dass Mittel zum Abstreifen des in die Zwischenfläche (e) eingespritzten Schmiermittels um die Einlassöffnung herum angeordnet sind, welche den Rotor (1) mit dem Einlass des Verbrennungsluft- und Breunstoffgemisches für die Kraftmaschine verbindet, wobei diese Abstreifmittel einen Einlassdichtungsring (29) umfassen, der am Umfang der Einlassöffnung angeordnet ist und sich durchgehend an der Aussenfläche des Ventilhahns (1) abstützt und fähig ist, das Innere der Einlassöffnung in bezug auf die Zwischenfläche zwischen dem Ventilhahn (1) und dessen Bohrung (4) zu isolieren, um das Mitreissen von Öl und gleichzeitig von flüssigem Treibstoff an der Oberfläche (8) des sich drehenden Ventilhahns zu vermindern.
8. Vorrichtung nach Anspruch 7, dadurch gekennzeichnet, dass der Dichtungsring (29) einerseits aus weichem Werkstoff mit günstigen Reibungseigenschaften in bezug auf die Ventilhahnoberfläche, wie Kunststoff, gefertigt ist und andererseits unter Einwirkung der wesentlich konstanten Kraft einer Feder (30) ununterbrochen an die Ventilhahnoberfläche angedrückt wird.
9. Vorrichtung nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass der Ventilhahn (2) zwei getrennte Durchlässe (36, 37) für den Einlass bzw. für den Auspuff besitzt, die nacheinander bei Drehung des Ventilhahns (1) brennkammerseitig am Dichtungsring (6), hingegen auf der der Brennkammer (2) entgegengesetzten Seite in Auslassöffnungen münden, deren jede auf der Ventilhahnachse in bezug auf den Dichtungsring (6) versetzt angeordnet ist, derart, dass das Mitreissen von Brennstoff auf der Ventilhahnoberfläche, sowie das Mitreissen von Brennstoff am Einlass in den im Inneren des Ventilhahns angeordneten Einleitdurchlass (27) vermindert wird.
10. Vorrichtung nach Anspruch 9, dadurch gekennzeichnet, dass die getrennten Einlass- und Auspuffdurchlässe (36, 37) zweier benachbarter Brennkammern im Ventilhahn derart angeordnet sind, dass sie in eine Verbindungsöffnung (38) münden, die mit dem Einlass oder dem Auspuff verbunden ist, welcher den beiden benachbarten Kammern gemeinsam zugeordnet ist, so dass die Anzahl an der Aussenfläche des Ventilhahns vorzusehender Öffnungen vermindert wird.
11. Vorrichtung nach einem der Ansprüche 1 bis 10, verwendet bei einem Viertakt-Verbrennungsmotor, dadurch gekennzeichnet, dass der Einlasskreislauf der Brennkammer (2) Mittel zum Unterbinden des Brennstoff einleitung in die Brennkammer eingesaugte Luft vor Beendigung des Einlasses aufweist.
12. Vorrichtung nach Anspruch 11, dadurch gekennzeichnet, dass bei Einlass des Brennstoffs durch Einspritzen in die Einlassluft die Mittel zum Unterbinden darin bestehen, dass die Brennstoffinjektion vor Beendigung der Ansaugphase völlig unterbunden wird.
13. Vorrichtung nach Anspruch 11 oder 12, dadurch gekennzeichnet, dass die Mittel zum Unterbinden wenigstens einen Hilfsdurchlass (39, 40) für brennstoffreiche Luft umfassen, der im Ventilhahn (1) und im Zylinderkopf (32) der Brennkammer angeordnet ist und an der Zwischenfläche zwischen dem Rotor (1) und dessen Bohrung (4) über eine Öffnung mündet, die vermöge der Drehung des Rotors (17 verschlossen wird, bevor die Haupteinlassöff- nung(en) (25) verschlossen wird (werden).
EP19850400107 1984-02-03 1985-01-23 Anlage zur Kontrolle für das Öffnen und Schliessen der Brennkammer einer Brennkraftmaschine Expired EP0152321B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85400107T ATE30456T1 (de) 1984-02-03 1985-01-23 Anlage zur kontrolle fuer das oeffnen und schliessen der brennkammer einer brennkraftmaschine.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
FR8410675A FR2549490A1 (fr) 1983-07-23 1984-02-03 Procede pour la fabrication d'une piece forgee en acier faiblement allie
FR8410675 1984-02-03
FR8500637A FR2576060B2 (fr) 1985-01-17 1985-01-17 Dispositif de controle de la circulation des gaz de et/ou vers une chambre de combustion de moteur a combustion interne
FR8500637 1985-01-17

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EP0152321A1 EP0152321A1 (de) 1985-08-21
EP0152321B1 true EP0152321B1 (de) 1987-10-28

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FR2643417B1 (fr) * 1989-02-17 1991-03-29 Elf France Ensemble de soupape pour moteurs a explosion
GB9000306D0 (en) * 1990-01-06 1990-03-07 Bullivant Nicholas T Rotary valve
ES2249068B1 (es) * 2002-06-10 2007-06-01 Antonio Ferreres Lopez Valvula de distribucion rotativa.
DE102005000034A1 (de) * 2005-04-15 2006-10-19 Ford Global Technologies, LLC, Dearborn Drehschieberventil für ein Kraftfahrzeug
US11242933B2 (en) * 2019-06-03 2022-02-08 Fisher Controls International Llc Floating valve seat for a rotary control valve for use in severe service applications

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FR628533A (fr) * 1927-02-04 1927-10-25 Porter Engine Dev Inc Perfectionnements aux moteurs à combustion interne
FR747013A (fr) * 1932-08-02 1933-06-09 Distribution par tiroir rotatif pour moteurs à explosion
DE902918C (de) * 1942-11-12 1954-01-28 Charlotte Heylandt Geb Wachter Abdichtung des beweglichen Zylinderbodens bei walzenfoermigen Drehschiebern
US4114639A (en) * 1973-09-07 1978-09-19 Cross Manufacturing Company (1938) Ltd. Lubricated rotary valve with concentric sealing rings
EP0100713B1 (de) * 1982-07-27 1986-11-12 Guy Negre Dichtungselement für eine Gaszyklus-Regelvorrichtung einer Brennkammer

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JPH0457845B2 (de) 1992-09-14
JPS60198315A (ja) 1985-10-07
DE3560844D1 (en) 1987-12-03
EP0152321A1 (de) 1985-08-21
BE901637A (fr) 1985-08-01

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