Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C1/00—Rotary-piston machines or engines
  • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
  • F01C1/063—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
  • F01C20/10—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
  • F01C20/14—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using rotating valves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
  • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

• the subject of the present invention is improvements relating to the management of the gaseous flows of the rotary engine as described in European patent EP 748 415 and in US Pat. No. 5,992,371.
• This rotary engine consists of an engine block in which is bored a cylindrical chamber in which is mounted in rotation a rotor with continuous movement, hollow, with two diametrically opposed recesses.
• an intermittent rotor formed of a shaft mounted on internal bearings of the rotor with continuous movement, and two radial vanes, diametrically opposed, engaged in the recesses of the rotor with continuous movement.
• the pallets form with the two evidences of the rotor with continuous movement, two working chambers called active chambers, diametrically opposed and two other so-called passive chambers diametrically opposed, these different chambers being of variable volume.
• active chamber evolves according to a thermodynamic cycle, a gaseous mixture introduced into each of these by a rotary valve when they come opposite an intake bore formed in the wall of the engine block, this gaseous mixture is removed after exhaust combustion.
• the exhaust gas exhaust bore is either free or associated with a rotary valve.
• the rotary plug is rotated, at an angular velocity twice that of the continuous rotor, by a pinion gear engaged with a ring gear coupled to the rotor with continuous movement.
• the prior arrangement does not provide any means, at the plug, adjusting the volume of gas introduced into the working chamber.
• the thermal machine with rotary pistons usable in particular as a combustion engine, spark ignition or diesel, comprising a motor unit in which is machined a cylindrical bore in which are mounted coaxially, in relation interpenetration device, two rotors which form with said bore at least one working chamber of variable volume, and at least one passive chamber behind the previous, subject to rotate about the geometric axis of revolution of the cylindrical chamber, and in which working chamber evolves according to a thermodynamic cycle a gaseous mixture capable of delivering during this cycle a motor work rotor continuously moving, said gas mixture being introduced into said chamber by passage through a radial inlet bore formed in the wall of the engine block, one of said rotors being continuous movement and the other intermittent movement, said pe intake reration being associated with a rotary plug intake system which rotary plug closes and releases alternately said drilling and this in accordance with the phases of the thermodynamic cycle, said rotary intake valve being rotatably mounted in a cylindrical chamber d a body, which is in
• this arrangement has the effect of increasing the speed of introduction of the gaseous mixture into the working chamber which allows a homogeneous filling of this chamber and improves the rate of combustion.
• the exhaust boring of the combustion gases is associated with an exhaust system comprising a rotary plug, rotatably mounted in the cylindrical chamber of a body, said rotary valve having an exhaust a wall of uniform thickness curved in an arc circumferential circle constituting a rotary shutter, the longitudinal edges of said wall defining a longitudinal opening, and said plug further comprising a terminal wall substantially in the form of circular disc, connected to the arc wall of circle circumference, said rotary plug being coupled by its end wall to a drive shaft coupled to a motion transmission coupled to the continuous motion rotor.
• a secondary exhaust is provided and this secondary exhaust is associated with a secondary exhaust system comprising a rotary valve driven by the rotor with continuous movement.
• FIG. 1 is a longitudinal sectional view of a thermal machine according to the invention
• FIG. 2 is a cross-sectional view along the line AA of FIG. 1,
• FIG. 3 is a perspective view of an intake system according to the invention.
• FIG. 4 is a longitudinal sectional view of an intake system
• FIG. 5 is a perspective view of an exhaust system
• FIG. 6 is a longitudinal sectional view of an exhaust system
• FIG. 7 is a cross-sectional view of an intake system according to a second embodiment
• FIG. 7a is a detail view according to an enlarged scale of the means for obtaining and adjusting the speed
• FIG. 7b is a view along the arrow F of FIG. 7a
• FIG. 8 is a longitudinal sectional view of the intake system according to the second embodiment
• FIG. 9 and 10 show in perspective, respectively, a rotary intake valve and a rotating exhaust bush.
• FIG. 11 is a sectional view of an engine, showing the intake and exhaust systems according to another variant embodiment
• FIG. 12 is a perspective view showing the rotary plug of the secondary exhaust system
• FIG. 13 is a sectional view of an air intake device
• FIG. 14 is a plan view, on a reduced scale, of a valve mechanism.
• thermal machine with rotary pistons, can be used in particular as a heat engine, for example the spark ignition type or diesel type.
• This machine comprises a motor unit 1 in which is machined a cylindrical bore 2 in which are coaxially mounted, in interpenetration relation, two rotors 3, 4 which form with said bore two working chambers 5 with variable volume, diametrically opposite and two passive chambers 6 of variable volume, diametrically opposed disposed respectively behind the two working chambers.
• the continuously rotating rotor 3 of cylindrical shape is provided with an axial bore 7 passing therethrough and two diametrically opposed radial recesses 8 formed from the outer cylindrical face towards the axial bore.
• the intermittent rotor 4 which is formed of a cylindrical shaft 9 having, at a distance from its two ends, two radial vanes 10 diametrically opposite.
• the shaft 9 is mounted on two end bearings formed in the bore of the rotor with continuous movement, and the radial vanes 10 are respectively engaged in the radial recesses 8 of the rotor with continuous movement 3.
• Each pallet 10, in association with the corresponding recess 8 and with the cylindrical inner face of the cylindrical bore 2 of the engine block forms a working chamber 5 and a passive chamber 6 located behind the previous one.
• the two rotors 3, 4 are kinematically connected to one another by appropriate mechanisms not described here, and are constrained to rotate in the same direction continuously for the continuous-motion rotor and discontinuously for the rotor to intermittent movement.
• the particular movement of each rotor is described in particular in patent EP 748 415.
• a gas mixture is introduced into each working chamber 5 to evolve according to a thermodynamic cycle in which a motor work is delivered to the rotor with continuous movement.
• This gaseous mixture is introduced into the working chamber by passage through an intake bore 11 formed radially in the wall of the engine block.
• the gaseous mixture is discharged from each working chamber 5 by passage through at least one exhaust bore 12 made radially in the wall of the engine block 2.
• the intake bore 11 is associated with an intake system 13 connected to a gas mixture supply line.
• This intake system comprises a rotary plug 14 provided for alternately closing and releasing the intake bore 11 and in accordance with the phases of the cycle. thermodynamic.
• This intake system is mounted in a blind cylindrical chamber 15 of a body which is in connection with a gas supply pipe on the one hand and with the through-hole admission 11 on the other hand.
• the cylindrical chamber 15, in which the intake system 13 is mounted can be formed in the engine block 1 but preferably this chamber is formed in a tubular body 16 attached to the engine block 1.
• This tabular body 16 is fixed by example by screw, to the cylindrical wall of the engine block, is provided with a longitudinal flat by which it is applied against a flat formed in the cylindrical wall of the engine block, the through-hole intake 11 being formed on the one hand in the wall of the tubular body 16, to the right of the flat part of the latter and secondly in the wall of the engine block to the right of the flat that includes the latter.
• the inlet through bore 11 is in the form of an oblong slot, the longitudinal axis of said slot being disposed along a generatrix of the wall of the chamber 2 of the engine block.
• the rotary plug 14 consists of a cylindrical element limited by two flat end faces and having an internal cylindrical chamber. This chamber opens on the one hand on one of the two end planar faces and forms on said face a circular front opening and on the other hand on the cylindrical planar face where it forms a longitudinal opening delimited by two parallel longitudinal edges. to the axis of rotation of the bushel and angularly spaced apart from each other. This opening, from one edge to another, extends along an arc with a circle circumference greater than 180 degrees.
• the rotary plug 14 has a transverse wall, terminal in the form of a circular disc. The rotary plug 14, through this wall, is coupled to a longitudinal drive shaft 17 coupled to a motion transmission itself coupled to the rotor 3 continuous movement, the plug being rotated at an angular speed double that of the rotor with continuous movement.
• the drive shaft 17 is engaged in bearings mounted in the tubular body 16.
• the motion transmission is constituted by a pinion gear 18 mounted in attachment on the drive shaft 17, and by a ring gear 19, coaxial with the rotor 3 with continuous movement and fixed thereto, with which the pinion 18 is engaged.
• the motion transmission consists of a toothed belt, wound on a first toothed pulley coupled to the drive shaft 17 and a second toothed pulley coupled to the rotor 3 with continuous movement.
• the intake system 13 associates with the intake bore 11 a member 20 for adjusting the gas passage section, this adjustment member 20 according to a first embodiment being interposed between the inner face of the the cylindrical chamber 15 and the rotary plug 14.
• the adjusting member 20 can be positioned on demand in a first complete closed position of the through-bore 11, in a second position of total clearance of said bore 11 and according to any one of the intermediate positions between the first position and the second position, these intermediate positions corresponding to the partial occlusion of the intake bore 11.
• the gas flow control member 20 comprises an endless cylindrical wall 201 of uniform thickness and a transverse end wall 202 provided with a gas introduction pipe 203, the endless cylindrical wall 201 being provided with a corresponding radial through-hole 204, in correspondence with total clearance or intermediate position, in relation to the through-hole 11 of the gas.
• This piercing 204 is preferably of oblong shape, the longitudinal axis of said shape being disposed along a generatrix of the wall 201.
• the rotary plug 14 is engaged in the internal volume delimited by the cylindrical wall of the regulating member 20, the end wall of said plug 14 and the end wall 202 of said member 20 being opposite to each other.
• the end wall 202 closes the blind cylindrical chamber 15 and the tubing 203 that said door wall is sealingly connected to the intake duct.
• the end wall 202 is external to the tubular body 16 and has at least one through oblong through-hole of circular circumference, in which is engaged the rod of a fixing screw engaged in screwing in a tapping of said body, said body adjusting member 20 being immobilized in translation by said screw and not in rotation and being associated with an actuating member in rotation in the direction of closing or disengagement of the intake bore 11.
• a vein 22 In the internal volume defined by the cylindrical wall 201 of the adjusting member 20, is mounted in attachment to the end wall 202 of said member, a vein 22 having an internal channel 23 for the passage of gases.
• This internal channel 23 is in relation on the one hand with the inlet manifold of the gases 203 that comprises the adjusting member 20 and on the other hand with the through bore 204 formed in the cylindrical wall of this adjustment member.
• This vein 22 has a cylindrical external shape and the rotary plug 14, by its cylindrical wall 141 is disposed between the cylindrical outer face of said vein 22 and the inner face of the cylindrical wall 201 of the adjusting member 20.
• the internal channel 23 of the vein 22 has at its end, facing the inlet pipe 203 a circular section and at its end opposite the through bore 204 an oblong cross section, the inner section of the channel passing gradually from one cross sectional shape and the cross sectional area of the channel being constant from one end to the other.
• FIGs 6 and 7, 7a and 7b is shown an intake system according to a second embodiment. This intake system is always mounted in a cylindrical chamber 15 formed in a body 16 which can be tubular and which can be attached to the engine block 1.
• the rotary plug 14 is rotatable about a cylindrical metal casing 60, fixedly installed in the chamber 15, the casing 60 having opposite the or through the through holes 11 an oblong through bore 61 disposed opposite the intake bore 11.
• the regulator 20 of the gas flow rate is constituted by a curved arcuate wall of circle circumference mounted in the cylindrical casing 60, able to slide on the internal face of said casing 60, and coupled to a control mechanism of the degree of closure of the bore 61 and consequently of the intake bore 11.
• the wall 20, by the control mechanism can be brought to the total position for closing the bore 61, in the disengaged position total of this drilling or partial closure position of said bore 61.
• the adjustment mechanism comprises a pinion 65 engaged with a ring gear sector 66 formed on the wall 20, said pinion being mounted on a control shaft 67 coupled to a controlled drive means pivoting in one direction or the other.
• the intake system will advantageously have means 62, 63, 64 for obtaining and adjusting an idle operation of the thermal machine.
• the means 62, 63, 64 for obtaining and adjusting an idle operation are constituted by a tongue 63 projecting into the channel 23 ', carried by a wall 62 curved in a circular arc circumference of circle mounted in the envelope cylindrical 60 and occupying a lateral position to the channel 23 ', and by an internal housing 64 formed in the wall 20 of adjustment and having a first opening formed in the front edge of the wall 20 and facing the tongue 63, and second and third openings formed respectively on the large curved faces of the wall 20.
• These second and third openings and the housing 64 form a gas passage section to the inlet port 11, in the closed position of the through bore 61
• the housing 64 in particular in the closed position of the bore 61, by the adjusting member 20 comes, through the first opening, to engage around the tongue 63.
• the wall 62 is able to slide on the face int.
• An envelope 60 and is associated with means for adjusting the degree of depression of the tongue 63 in the housing 64 and consequently the degree of depression of said tongue 63 in the section of passage of the gas between the second and the third openings.
• the adjustment means consist of a ring gear sector 68 formed on the wall
• the tongue 63 as can be seen in Figures 7 and 7a protrudes on that of the two banks of the wall 62 facing the channel 23 '. This tongue occupies only a small portion of the length of said bank.
• a stream 22 ' having an internal channel 23' for the passage of gases which is in relation on the one hand with the intake manifold 203 of the gases and on the other hand with the
• This internal channel 23 ' has at its end opposite the intake pipe 203, a circular section and at its end with respect to the through-hole 11, a cross-section of the casing 60. oblong right, the inner section of the channel gradually passing from one sectional shape to another and the area of the cross section of the channel 23 'being constant from one end to the other.
• the internal channel 23 ' comprises a series of partition walls 231' defining a plurality of passage sections 232 'and the inlet bore 11 is formed by a plurality of oblong slots, aligned and separated from each other, the passage sections 232' opening respectively to the right of these oblong lights.
• the vein 22 will be provided with two external recesses intended to receive the walls 20 and 62. These walls can slide in these recesses.
• an exhaust system 24 comprising a rotary valve 25, rotatably mounted in the blind cylindrical chamber 26 of a body 28.
• This rotary exhaust valve 25 has a wall 251 of uniform thickness bent in circular circumference arc constituting rotary shutter.
• the wall 251 has two longitudinal edges delimiting a longitudinal opening developing in an arc with a circle circumference greater than 180 degrees.
• This plug further comprises an end wall 252 substantially in the form of a circular disk, connected to the arc wall of circular circumference, said bushel rotary coupling being coupled by its end wall 252 to a drive shaft 27 coupled to a motion transmission itself coupled to the rotor 3 with continuous movement, this drive shaft being engaged in two bearings mounted in the body 28.
• the rotary plug 25 is rotated at an angular velocity double that of the continuous motion rotor.
• the body 28 in which the cylindrical chamber 26 is formed is tabular and is fixed by screw to the cylindrical wall of the engine block.
• This tubular body is provided with a longitudinal flat by which it is applied against a flat formed in the cylindrical wall of the engine block, the exhaust through bore 12 being formed on the one hand in the wall of the tubular body 28, on the right of the flat part of the latter and secondly in the wall of the engine block to the right of a flat that includes it.
• the exhaust system 24 comprises, in addition to the rotary plug 25, a tubular exhaust pipe 29 comprising a portion 291 internal to the chamber 26 of the body 28 and an outer portion 292 to the body.
• the inner portion 291 is of tabular form and is engaged coaxially in the rotary plug 25.
• This internal tabular shape has the right of the through exhaust bore formed in the engine block, a radial through bore.
• the outer portion 292 has, externally to the chamber 26 of the body, a flange 293 for bearing and fixing to said tabular body 28.
• a vein 30 is mounted in fixing in the internal tabular form 291 of the exhaust pipe 29.
• This vein 30 has an internal channel 31 for the passage of combustion gases. This channel at one of its ends is in relation with the radial through bore formed in the internal cylindrical shape 291 of the exhaust pipe and at its other end is in relation with the internal volume of the outer portion 292 of the pipe of exhaust.
• the exhaust through bores of the combustion gases, formed respectively in the engine block 1 and the tabular body 28, and in the internal part of the exhaust pipe are each in the form of an oblong slot and the end corresponding channel 31 located opposite these through holes is also in an oblong form.
• the transmission of motion between the shaft 27 and the rotor with continuous movement 3 is constituted by a toothed pinion 50 fixed to said shaft 27 and meshing with the ring gear 19.
• This transmission of motion may be constituted by a toothed belt wound on a first toothed pulley coupled to the drive shaft 27 and a second toothed pulley coupled to the rotor 3 continuous movement.
• the flow of gas through these is diametrical.
• the wall of the cylindrical chamber 15, 26 of each intake and exhaust system 24 has diametrically opposite with respect to the intake or exhaust bore formed in the engine block 1, an oblong through hole for passing gases.
• the gas regulating member 20 will be formed of a cylindrical member rotatably mounted in an axial bore formed in the deflector 131 in secant manner to the diametrical bore of the latter.
• the member 20 will be provided with a diametrical oblong through hole intended to come by rotation of said member to release the passage of the gas or to seal it partially or possibly in totality.
• the engine block 1 is equipped with at least one secondary exhaust bore 12a independent of the first exhaust bore 12 and disposed downstream of the latter, said second bore being provided for the evacuation of a fuel gas. cooling introduced into the passive chamber, gas leaks and possibly the remaining flue gases still present in the working chamber.
• the cooling gas is air and this gas is introduced into the passive chamber by a longitudinal channel formed in the cylindrical shaft 9 of the rotor 4 intermittently and by radial channels formed in this shaft.
• a secondary exhaust system 24a comprising a cylindrical chamber 26a in which is rotatably mounted a rotary valve 25a driven in rotation by the rotor with continuous movement and this via an appropriate movement transmission.
• This rotary plug 25a externally to the cylindrical chamber 26a will cooperate with a motion transmission engaged with the rotor with continuous movement.
• a deflector 241a consists of a cylindrical body in which are formed diametrically two separate through holes. Preferably these holes are formed according to a common diametral plane.
• the rotary plug 25a has two diametrical through-holes respectively formed in two diametral planes angularly offset with respect to each other intended to correspond respectively with the two bores of the deflector, and the cylindrical chamber 26a, diametrically opposite to the secondary exhaust bore has two separate drain holes respectively aligned with the bores of the baffle.
• the secondary exhaust system 24a has two gas discharge paths, alternately open and closed by the rotary plug.
• this arrangement allows the evacuation on one of the two ways of the burned gases still present in the working chamber and in a second step, on the other way, the evacuation of the secondary air which can be used to achieve post combustion, supercharging and other.
• the deflectors 241 and 241a of the primary 24 and secondary 24a exhaust systems will be provided with a plurality of through channels for circulating a cooling fluid.
• the machine will include an air inlet device 700.
• This air inlet device 700 will be fixed by any known means to the engine block 1 and around the end of the shaft 9 of the rotor 4 to move intermittent.
• This device will consist essentially of a housing 701 comprising a cylindrical internal chamber 702 in which will be housed a toroidal air filter 703.
• the casing 701 of cylindrical shape will include an end wall 701a and an envelope wall 701b rooted at the end wall 701a.
• This envelope wall will comprise radial through holes 704 of air inlet.
• the end wall 701a will be provided with a central through bore 705 through which it will be engaged around the shaft 9 and with several through bores 706 made around the central bore 705.
• This end wall 701a will receive externally to the internal volume of the housing, a cap 707 defining a sealed chamber 708 in which will be mounted a valve mechanism 709 associated with the through holes 706.
• This sealed chamber will be in relation with the internal volume of the shaft 9.
• the valve mechanism 709 will be constituted by flexible strips 709a or semi-rigid able to come close or clear the through holes 706, these lamellae being rooted in a circular ring 709b provided to be clamped between the cap 707 and the end wall 701a, this ring being able to constitute seal.
• the rotary bushings of the intake or exhaust systems can be driven at an angular velocity twice that of the continuously moving rotor. Alternatively, they are driven at the same angular velocity.
• the latter is advantageously arranged in a pre-ignition chamber 331 adjacent to the chamber 2 and in communication with the latter by at least one through-hole 333, the gaseous mixture, in compression phase in the working chamber to fill the pre-ignition chamber.
• the ratio of candle diameter and bore diameter is from 3 to 12.
• the pre-ignition chamber is formed in a spark plug holder 33 engaged in a radial through bore of the engine block.
• This candle holder 33 is provided with an internal cavity in which is engaged the spark plug and in which is reserved a free volume in which are located the electrodes of the candle, this internal cavity and more particularly the free volume constituting the chamber 331.
• the internal cavity 331 and the free volume are in communication with the working chamber 5 by at least one through hole 333 preferably rectilinear.
• the free volume of the candle holder 33 is filled with gaseous mixture.
• the gaseous mixture contained in this free volume is ignited spontaneously and the flame propagates in the form of a jet at high speed, through the hole or holes 333, to the working chamber 5.
• a system 40 for treating the combustion gases may be associated a system 40 for treating the combustion gases.
• This system consists essentially of a catalyst 401 of the two-way or three-way type, for example, sealingly connected by any known means to the outer portion 292 of the exhaust pipe.
• This catalyst 401 converts the combustion gases by reduction and oxidation.
• the transformed gases can be further loaded with HC (unburned hydrocarbons), CO (carbon monoxide) and NOX (nitrogen oxide).
• the cooling air delivered by the secondary exhaust is injected into the stream of hot gases delivered by the catalyst in order to carry out a post combustion by oxidation of HC, CO and NOX.
• an afterburner chamber 402 is provided in which the secondary exhaust stream and the combustion gases are introduced on the one hand.
• the catalyst 401 will be interposed in a sealed manner between the outer portion of the exhaust pipe and the afterburner chamber 402.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Exhaust Gas After Treatment (AREA)

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• 2006
  • 2006-05-12 EP EP06764610A patent/EP2021583A1/de not_active Withdrawn
  • 2006-05-12 WO PCT/FR2006/001067 patent/WO2007132070A1/fr active Application Filing

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