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
  • F01L7/18—Component parts, details, or accessories not provided for in preceding subgroups of this group
• • 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
  • F01L7/026—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves with two or more rotary valves, their rotational axes being parallel, e.g. 4-stroke
• • 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
  • 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 relates to an internal combustion engine with rotary distribution shutters.
• an ult ic li ndre internal combustion engine comprising a group of in-line cylinders, the combustion chambers of which each communicate with an intake orifice and with an exhaust orifice, the orifices of inlet, on the one hand, and the exhaust ports, on the other hand, of said group of cylinders being arranged in alignments, the distribution means allowing the opening and closing of said intake and exhaust ports comprising two rotary nozzles, of circular section, each comprising a plurality of aligned hollow shutters, rigidly connected to one another and communicating with each other, and the side wall of which is provided with a plurality of spaced apart lights, angularly offset , and the number of which corresponds to that of the cylinders to be served, one of these rotary nozzles allowing the opening and closing of the alignment of intake orifices of the group of cylinders, while the second allows the opening and closing of the alignment of exhaust orifices of said group of cylinders.
• Each rotary nozzle is made up of alternating cylindrical portions of different diameters, the gas passage openings being provided in the portions of reduced diameter.
• Each rotary nozzle of distribution is housed in a fixed sheath and its larger diameter portions are dimensioned to have a well-adjusted rotation and sliding clearance inside said fixed sheath, these larger portions being provided, near their ends, with sealing rings allowing a tight seal to be established for the passage of gases.
• Another drawback of the device described in the aforementioned document lies in the fact that one is obliged to place the carburetor or the exhaust at one of the ends of the rotary distributing tubular rods, which constitutes a constraint when the engine must register in a reduced volume.
• An object of the present invention is to remedy the drawbacks outlined above of mu It i cy li ndre internal combustion engines, with a - 3 -
• this objective is achieved thanks to an engine of this kind, more particularly remarkable by the fact that the rotary intake nozzle and the rotary exhaust nozzle are housed, the first, in an intake manifold and , the second, in an exhaust manifold each forming a chamber or space surrounding, respectively, said intake nozzle and said exhaust nozzle, over a large portion of their periphery, these chambers being so separated sealed and arranged so as to allow gas circulation outside and along said rotary nozzles.
• the circulation of gases takes place both inside and outside of the rotary distribution nozzles, in the space formed between the latter and the internal surface of said manifolds, in which turns the gas stream (fuel and / or oxidizer), so that, in the case of supply, all the cylinders are supplied in substantially the same conditions, both in volume and in quality of the gas mixture, if although you get better combustion and better engine balance.
• each intake and exhaust port is equipped with at least one movable seat making it possible to modify the cross section of the fluids, as well as the moment or instant of closure or of L opening of said orifice, and adjustment means make it possible to adjust the position of these movable seats, these means comprising a cylinder installed, in a sealed manner, through the sealed wall separating the intake and exhaust manifolds, and in which is housed a piston subjected to the action of a compression spring tending to push it in the direction of the exhaust manifold, at least one of the faces of this piston being connected, by means of a * articulation, to a control rod itself connected to a connecting rod wedged on a shaft on which are also wedged connecting rods, each connected by means of a transmission linkage to at least one of the mobile seats. At least one of the rotary shutters.
• Figure 1 is a longitudinal sectional view of the upper part of a cylinder equipped with a dispensing device according to the invention.
• Figure 2 is a perspective view of an embodiment of a rotary distributor nozzle consisting of two shutters arranged in the extension of one another.
• FIG. 2a represents, by two axial half-sections, two other examples of the configuration of a rotary distributing nozzle consisting of two obturators assembled in the extension of each other.
• Figure 3 is an axial sectional view of the drive nozzle of a rotary nozzle.
• Figure 3bis is a front view of the end of this tip.
• Figure 4 is an axial sectional view of an embodiment of the opposite nozzle of the nozzle.
• Figure 5 is a plan view in section of a dispensing assembly according to the invention.
• Figures 6 to 9a i llustrate the operation of the distribution system according to the invention.
• Figure 10 is a schematic view, in plan and in section, of an embodiment of rotary intake and exhaust nozzles fitted to the upper part of a four-cylinder engine.
• FIG. 10 bis is a diagrammatic view on a larger scale on line 10-10 in FIG. 10.
• Figure 11 is a perspective view in section i llustrant a control device of the seat adjustment system mobi the rotary shutters.
• Figure 12 is a cross-sectional view of a rotary shutter and its movable seats.
• Figure 13 is a perspective view of one of these movable seats.
• Figure 14 is a front view of a lateral flange for guiding movable seats.
• FIG. 1 shows the upper part of a cylinder 1 and a cylinder head 2 fixed to the upper part of this cylinder and delimiting the combustion or explosion chamber 3.
• the intake 4 and exhaust 5 ports are themselves provided with seats 6, 7, respectively, shutters.
• the shutters consist of rotary elements 8, 9, hollow, of circular section, in the side wall of which is provided a light 10, 11, respectively, for each cylinder of the engine to be served or served. These shutters can have a cylindrical, or conical, or ovoid, or even spherical shape.
• two or more of two rotary shutters 8, 9 are assembled in succession and in alignment, for example by screwing or otherwise.
• FIG. 2 illustrates two cylindrical rotary shutters 8a, 8b assembled one after the other and intended to equip a twin-cylinder engine.
• the assemblies T thus produced will be designated under the name of "rotary nozzles" in the description which follows, in order to facilitate the description.
• FIG. 2bis shows two other examples of conformation of the rotary distributor nozzle T consisting of two shutters 8 or 8 ′ assembled in the extension of one another, with a sliding capacity of amplitude limited relative to the Another, by means of simple grooves 61, which makes it possible to solve the problems which could arise from the effects of expansion or from a slight misalignment.
• the shutters 8 of the lower half-cut have a concave conformation, while the shutters 8 'of the upper half-cut have a bulged shape in their central part, such a shape increasing the capacity of introduction of fresh gases into the cylinders.
• FIG. 10 shows rotary nozzles for intake T-8 and exhaust T-9 each consisting of an alignment of four shutters 8a, 8b, 8c, 8d, or 9a, 9b, 9c, 9d, respectively , whose lights 10a, 10b, 10c, 10d or 11a, 11b, 11c, 11d are offset by 90 degrees.
• the shutters such as 8a, 8b, 8c, 8d, ...., thus aligned and integral with one another in rotation, constitute a tubular assembly according to which said shutters are in permanent communication by their bore.
• the rotary nozzles T-8 and T-9 can be arranged and di mens i on Amsterdams to serve r or serve a variable number of cylinders whose axes may or may not be parallel.
• Each nozzle T is, for example, made up of tubular pieces of machined steel and the exterior and, if necessary, interior surfaces, can be provided, over all or part of their length, with a coating of ceramic or other material capable of withstand thermal and other shocks, during the phases: explosion, expansion and exhaust, in particular in the case of an internal combustion engine.
• One of the ends of the nozzles T-8 and T-9 is provided with a drive and guide nozzle designated as a whole by the reference 12 (FIG. 3), while the opposite end of the said nozzle can be provided with a closing end piece 13 (FIG. 5) which may consist of a simple plate fixed in a leaktight manner, by screwing, on said end, or with a end piece 14 comprising a tubular axial extension 14a (FIG. 4) allowing , depending on the case> its connection, for example by means of a seal rotary, to a fuel mixture rear pipe or to an exhaust pipe.
• Each rotary nozzle T-8 and T-9 thus produced and equipped, comprises, according to the embodiment of Figures 2 and 5, at a distance from its portions provided with the lights 10 or 11, parts of smaller diameter 15a, 15b , 15c (FIG. 2) on which the inner rings of the bearings 16a, 16b, 16c are fixed ensuring the guiding in rotation and the positioning in translation of said nozzles.
• the outer rings of these bearings are fixed to the housing wall described in the rest of this description and formed in the cylinder head 2.
• the aforementioned bearings could be replaced by rings.
• Each bearing 16a, 16b, 16c or outer friction ring is surrounded by two eccentric and concentric rings 17, 18 of which at least one can be driven in rotation, with however the possibility of limited angular movement.
• This assembly, bearing and rings, is maintained and guided, at the bearings, between two pairs of half-shells The 19.
• One of the half-shells The of each of these pairs of half-shells 19 is provided of a lug 19a.
• These lugs 19a penetrate into one of the faces of one and the other of the two eccentric rings, so that a movement movement is obtained which tends to move away or bring the rotary nozzle T-8, T- 9 of the seats 6, 7 (which are described in more detail in the remainder of the present description), by a simple rotation of these half-shells, the method of fixing on the cylinder head makes it possible to multiply the angular positions.
• This end piece 12 has a smooth bearing surface 25 on which the inner ring of the roule ⁇ ment 16a and a shaft 26 on which is fixed, for example by keying, a toothed pulley 27 driven by toothed belt or a pinion driven by chain.
• the outer end 26a of this steel end piece can be machined or shaped ( Figure 3bis) so as to be able to drive an igniter, for example of the Delco type (Registered Trademark) or another device necessary for the operation of the engine.
• These spark plugs 28 can be installed vertically or with a certain angle in the axial plane of the cylinder head, in two passages reserved therein and opening into the combustion chamber.
• the second perforation made in the cylinder head and ending in the combustion chamber can be used to accommodate a glow plug or the like.
• nozzles 12 can be coupled to the pump drive device injection of diesel engines or be used for other functions such as, for example, controlling a direct injection device.
• Access to the nozzles 12 and 13 of the nozzles is extremely easy after removing the front plates 29 or rear 30 of the cylinder head 2.
• Lubrication of the guide bearings of the rotary nozzles is carried out from the lubrication network supplied by the engine oil pump located in the crankcase. Oil, through a conduit opening into the bearings, retained by the half-shells.
• the 19 blocking the concentric rings and the external cages of the bearings, fulfills its function and returns to the crankcase by another free conduit. and largely dimensioned.
• Each obturator element of each of the nozzles T-8 and T-9 has a cutout or lumen 10 or 11, respectively, carefully calibrated and dimensioned and which, during the rotation of the nozzle, communicates periodically with one of the orifices 4 or 5 opening into the combustion chamber of one of the cylinders, according to the function assigned to the nozzle, this orifice being closed by the cylindrical wall of the shutter between two passages of the light.
• the light 10 or 11 when the light 10 or 11 has left the position of communication with the orifice 4 or 5 for access to the combustion chamber 3, it opens into the cavity 31 or 32 surrounding the rotary nozzle T-8 or T-9, respectively.
• the T-8 intake and T-9 exhaust nozzles are placed in two adjacent shaped cavities cylindrical or other, formed in the cylinder head 2 and separated in a sealed manner from one another, these cavities constituting, respectively, the intake manifold 31 and the exhaust manifold 32.
• These intake manifolds 31 and exhaust 32 are formed by longitudinal chambers or spaces which surround The rotary inlet nozzles T-8 and exhaust T-9, respectively, over most of their periphery, these longitudinal chambers or spaces allowing circulation gases outside and along said nozzles distribu ⁇ trices. It is understood that, in this way, the gases can circulate freely both inside and outside the nozzles.
• the cages 63 which ensure the positioning of the assemblies 16-17-18 constituting the bearings of said nozzles and more particularly the cages receiving the intermediate bearings between cylinders, are not waterproof, but perforated or provided with passages 62 allowing this Free movement ( Figures 10 and 10a).
• the lights 10, 11 of each pair of twin shutters 8, 9 of the rotary distribution nozzles T-8, T-9 have a position angularly offset relative to each other, to allow them to fulfill the function assigned to them, ie "Admission” and “Exhaust”, respectively.
• the rotary nozzles T-8 and T-9 are rotated at a speed which is half that of the latter, as indicated previously, so that each of them performs a U-turn when the vi lebrequin completes a turn.
• the supply and exhaust ducts communicating with the intake 31 and exhaust 32 collectors, are connected to the side walls 21 of La or the cylinder heads 2 or to the cover (s) 33 covering it or these, which may have orifices 58a, 58b, respectively, for connection to the conduits for the arrival of fresh gases or for the discharge of burnt gases (not shown).
• This or these covers on the upper part, joining in the axis of the sealed central partition 34 separating the rotary nozzles T-8 and T-9, are, on the one hand, fixed on one side on this last, and for the other sides, screwed on the cylinder head (s) leaving Free
• the heads of the tightening bolts and the orifices for spark plugs, injectors or others are, on the one hand, fixed on one side on this last, and for the other sides, screwed on the cylinder head (s) leaving Free
• the heads of the tightening bolts and the orifices for spark plugs, injectors or others are, on the one hand, fixed
• the intake system and the exhaust system are separated in leaktight manner by the central partition 34, as indicated previously.
• Figures 6-6a, 7-7a, 8-8a, 9-9a are views associated in pairs and schematic illustrating the four-stroke cycle of an engine equipped to explo ⁇ sion of the dispensing device according to the in- • vention, considering a single cylinder of said engine.
• the piston P is at TDC (top dead center) at the end of its ascent stroke ending a four-stroke cycle.
• the lumen 11 of the rotary exhaust shutter 9 still communicates with the cylinder 1 while the lumen 10 of the intake shutter 8 enters into communication with said cylinder.
• the piston P descends, the rotary exhaust shutter 9 closes the exhaust port 5, while the rotary intake shutter 8 communicates, through its lateral light 10, with cylinder 1 into which the fuel mixture is sucked.
• Second step compression ( Figures 7 and 7a)
• the piston P is at PMB (bottom dead center)
• the exhaust port 5 is completely closed by the rotary exhaust shutter 9, while the light 10 of the rotary inlet shutter 8 still communicates, through a passage of reduced section, with the cylinder 1.
• FIG. 7a which shows the piston 1 during its ascent stroke
• the exhaust orifices 5 and d admission 4 are hermetically closed by the rotary exhaust and inlet 9 intake shutters 8, respectively; the gases are compressed in the upper part of the cylinder.
• Third step explosion and relaxation (figures)
• the piston P is again at TDC.
• the exhaust 5 and intake 4 orifices are always closed by the exhaust 9 and intake 8 shutters, respectively.
• the ignition of the compressed mixture caused before the piston P does not reach TDC causes the explosion which propels the piston P downwards (figure 8a).
• the piston P is again at PMB, the lumen 11 of the rotary shutter of escapement enters into communication with the orifice of escape 5 of cylinder 1, the burnt gases begin to s '' flow outward.
• the piston is being raised, the light 11 communicates with the exhaust orifice 5, the burnt gases remaining in the cylinder are expelled by said piston.
• the lumen 11 of the rotary exhaust shutter 9 comes into contact with the exhaust port 5 and allows the flow of gases burnt outwards under the effect of Them detent (advances to the opening of the exhaust shutter).
• each inlet 4 and exhaust 5 are equipped with at least one mobi seat on 6 or 7 enabling the cross section of the fluids to be adjusted and, preferably, two seats mobi likely to be brought closer to reduce this section or distant from each other to increase it.
• the adjustment of the distribution device described above is obtained by means of a system for adjusting the position of the seats 6 and 7 of the rotary shutters 8 and 9, respectively, making it possible to modify the passage times of the fluids by decreasing or increasing the section of the access opening to the inlet 4 and exhaust 5 ports. It can be seen that the adjustment of the position of the seats 6 and 7 also makes it possible to adjust the moment or instant of the closing and / or opening of the intake and exhaust ports.
• an adjustment device according to which all the functions for modifying the position of the movable seats are contained and actuated inside the cylinder head, in the volume existing between the latter and the rotary nozzle T- 8 or T-9 and constituting the intake manifold 31 or exhaust manifold 32.
• the operating command allowing to modify, during operation, the position of the movable seats can be obtained by means of the adjustment device described below and shown in FIG. 11.
• This device which is very simple in design, consists of a cylinder 36 in machined metal, fixed through the sealed transverse wall 34 separating the intake 31 and exhaust 32 collectors.
• the cylinder 36 comprises, for example in its intermediate part, a flange 37 provided with holes and allowing its fixing, by means of screws 38, on said wall.
• the part of the cylinder located in the exhaust manifold 32 is preferably as small as possible.
• the bottom of the cylinder, "Exhaust" side is closed by a plug 50 removably fixed on the end of the cylinder, for example by screwing, this plug having a hole 39 allowing the passage and the movement of a control rod.
• the passage 39 traversed by the rod 40a will be provided with an O-ring, since, in this case, the depressive effect will be canceled.
• the opposite bottom of the cylinder has an internal shoulder 46 against which is wedged One of the ends of a compression spring 47 the other end of which rests against the piston 42, this spring having the function of pushing said piston in direction of the exhaust manifold 32, when the pressures or depressions decrease or cease.
• this spring (diameter, diameter of the wire, and not the number of 'turns, length, material) are determined depending on the desired uti lisation and mid location wherein it travai lle.
• the compression of this spring can be modified by the simple addition of one or more round l Les-ca placed in the bottom of the cylinder, against the shoulder 46.
• the end of the spring oriented towards the inside the cylinder 36 is housed in a groove created in the bottom of the piston which also has a guide portion 42a of reduced diameter, oriented towards the shoulder 46 and opposing the possible buckling of said spring.
• the plug 50 makes it possible to avoid excessive displacement of the piston 42 under the effect of the spring 47. It also protects the piston from heat, while its central hole 39 allows both the movement of the rod 40a and the passage of the gas acting on the bottom of said piston.
• the piston is provided, for example in the vicinity of each of its ends, with a sealing segment 48 executed in nitrided cast iron or other material.
• the piston 42 also includes a peripheral recess 49 provided between the grooves of the sealing segments 48, this recess being intended to be filled with a THT grease, during assembly or possibly subsequently, by means of a grease nipple (not shown ) opening into the cylinder 36.
• the face of the piston 42 oriented in the direction of the intake manifold 31 is preferably also subject, by means of a joint and, for example, by means of a spherical joint, to a rod 40b, comparable to La rod 40a, and itself connected to a link-shaft-link-assembly similar to that previously described.
• the rods 40a and 40b can have an adjustable length and be arranged in any manner known per se to present this characteristic.
• rods 44 and / or 59 can be of different lengths and placed in function needs and in various positions, on the shaft 45, according to the amplitude of the movement that one wishes them to transmit, it being understood that one can, if necessary: - increase the capacity of the cylinder assembly 36 piston 42, developing its diameter;
• the shaft 45 is connected to the mobi seats 6 and 7 of the shutters 8 and 9, respectively, by means of the rods 59 and of a rod 60, to the transmission linkages 51 acting directly on the said shutters and one mode of which is The execution is visible on the right part of Figure 1.
• These seats 6, 7 have a curved shape, as can be seen in particular in FIGS. 1, 12 and 13.
• This machining contributes to creating a regular space between the rotary nozzle T-8 or T-9 and the movable seats, respectively 6 or 7, whatever its position.
• the movement of the latter, under the action of the rods which control their movement, between the cylinder head block and the rotary nozzle to which they are assigned, is thus perfectly controlled.
• Each end of a movable seat is limited in its lateral displacement, by a lateral flange 52 which also serves to improve the seal between the movable seat 6 or 7 and the rotary nozzle T-8 or T-9.
• the lateral flanges 52 have, on their internal face, a curved groove 53 in which is engaged a lug 54 which laterally comprises the seat mobi 6 or 7 and which limits the movement of said seat.
• the ceramic layer reinforced with the nozzles T-8 and T-9 only touches a tiny part of the movable seats 6 or 7 whose length, width and thickness are determined according to the diameter of the cylinder served .
• the seats 6 or 7 being subjected to thermal and other shocks and to chemical aggressions, are also treated to be able to resist these harmful actions by using, either, preferably, ceramics armed with suitable mixtures, or high-strength steels combined with special products.
• the seats 6 or 7, of curved shape as indicated above, are extended, opposite their free edge, by spaced rods 55, also curved and arranged at equal distance from the lateral edges of said seats, these rods comprising a head 55a by means of which they are connected, by means of an articulation, to the linkage 51 (right side of FIG. 1) or to the control levers 35 (left side of FIG. 1), according to the command option adopted to obtain the displacement of the movable seat elements 6 or 7.
• the invention provides a significant improvement over traditional valve distribution systems, because it allows the elimination of the latter and all of their springs or other return systems, which allows to consider a significant increase in rotational speed of the motors and their efficiency.
• This cavity by its shape and by its volume clearly greater than that necessary for the proper functioning of the complete rotary assembly and its seats as well as all the organs influencing the position modification of these, ensures Free Transfer gases from any point to another inside this cavity, around the rotary assembly and in the midst of the ancillary members allowing and facilitating the path of the gases towards the cylinder or cylinders also supplied by the inside of the rotary assembly. It can be perforated as required in multiple places and connected at one or more points with the external air or gas mixture inlets necessary for the proper functioning of the engine.
• the other cavity, forming a common collector 32 for the outlet of the burnt gases, contains the rotary assembly T-9 and its seats 6, 7 movable or not, replacing the exhaust valves and all the operating devices of the latter.
• This cavity 32 the shape and volume of which can be totally different from that of the cavity 31, must very easily contain the rotary assembly, the movable seats or not, as well as all the organs influencing the position modification of these last ; it ensures the free transfer of burnt gases, from any point to another, inside of this cavity, around the rotary assembly and in the midst of the ancillary members, allowing and facilitating the path of the burnt gases from the cylinders to the outside, very significantly improving their evacuation, also being done from the inside of the rotary assembly.
• It can also be perforated as required in multiple locations and connected at one or more points with one or more gas discharge conduits.
• the implementation of the invention does not require any substantial modifications.
• the external parts of the cylinder head (s) may, however, in this case be provided with blades of appropriate shapes and dimensions to remove the excess calories and ensure good cooling of the cylinder head (s) of this type of engine.
• the pre-heating of the intake fluids is ensured, as soon as it is put into operation. of the engine, by the heat input transmitted by the middle partition of the exhaust zone to the intake zone, which prevents icing in the latter.
• This central partition is used, furthermore, in the other direction, for a transfer of appreciable frigories, thus allowing cooling of the burnt gases.
• These intakes of calories or frigories can be increased, according to the needs, either by the provision of wings judiciously placed, or by a reduction of the thickness of this partition, or still by its partial replacement by a part of exchange made of a metal with a higher coefficient of heat conductivity.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Cylinder Crankcases Of Internal Combustion Engines (AREA)

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• 1994
  • 1994-03-25 FR FR9403932A patent/FR2717857B1/fr not_active Expired - Fee Related
• 1995
  • 1995-03-23 DE DE69503042T patent/DE69503042T2/de not_active Expired - Fee Related
  • 1995-03-23 WO PCT/FR1995/000362 patent/WO1995026460A1/fr active IP Right Grant
  • 1995-03-23 AU AU21417/95A patent/AU2141795A/en not_active Abandoned
  • 1995-03-23 US US08/704,674 patent/US5690069A/en not_active Expired - Fee Related
  • 1995-03-23 EP EP95914408A patent/EP0750719B1/de not_active Expired - Lifetime
  • 1995-03-23 JP JP7524999A patent/JPH09510765A/ja active Pending

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