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
  • F01C1/22—Rotary-piston machines or engines of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth- equivalents than the outer member
• • 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
  • F01C1/077—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 having toothed-gearing type drive
• • 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
  • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
  • F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
• • 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
  • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines

Definitions

• VUA we show an example of this way of doing things applied to a straight rod engine.
• a similar arrangement but this time connected to a master gear, or of an internal type support, can offer us a retroactive type design, such as a triangular motor here.
• this section we add a third way, by hoop gear, to support the blades of poly inductive machines, and produce a more global synthesis of these, in particular by producing post rotary machines in a retro-rotary manner
• the purpose of this section is to show how, following the generalizations that we have produced between retro rotary and post rotary poly inductive motors, we can now perform a synthesis so as to group the qualities of each set so that each can be applied to all engines to maximize power and efficiency.
• each type of engine can benefit from the qualities of the complementary category of engines.
• the retroactive motors have great qualities on the post active motors in that they harness the rear effect forces to transform them into front forces, which makes the surface of the blade exposed to the explosion generating energy over its entire length (FIG. IV C)
• Figure VI C shows that there is a significant improvement in the forces in such a poly inductive way of making a blade motor. This realization shows that if the geometric aspect can be linked, the technical way of realizing the forces of the machine is totally different.
• the present invention will attempt to do better, by attempting, as in the case of polyinductive retro rotary motors, to use positively the entire blade surface.
• a first embodiment will attempt this by going to act inside the crankshaft and the blade to obtain the desired effect retroactively (Fig. XI C) Since we now know that it is in relation to the crankshaft and not in relation to the body of the engine that the feedback effects must occur.
• An additional configuration of the present invention will also use in the semi-transmission an internal gear for one of the axes, The inversion being produced by the internal gear, the pivot gear will only be reducing and not reversing.
• a transverse axis will be installed, this axis being provided at each end with an induction gear, each being coupled to an internal gear, one located in the sidewall of the engine, the other in the side of the blade.
• this rule will first of all show that all poly inductive motors can be divided into two main categories depending on whether they are retro rotary or post rotary. Then it will aim to show that an unlimited number of rotary and post rotary motors can be achieved, and that to do this you simply have to respect the law of sides, a rule which will specify the precise relationships between the number of sides of the blades and those of the cylinders in which they will be placed.
• the master gear used is of the external type.
• the blade therefore rotates in the same direction as that of the semi-transmission membrane.
• the present invention intends to enact, what we will call the rule of the sides.
• This rule at the same time as it will allow us to group and geometrically distinguish the two major classes to which it will refer, will also allow us to show the possibility, while respecting this rule, of constructing infinite variables of these same engines.
• retro rotary motors can be made to infinity, always using a blade whose number of sides is greater than one of that of the cylinder in which it operates.
• a two-sided will evolve retroactively in a one-sided cylinder
• a three-sided blade will evolve in a two-sided cylinder.
• a four-sided blade will evolve in a three-sided cylinder.
• a six-sided blade in a five-sided cylinder a seven-sided blade in a six-sided cylinder.
• the master gear will be the same number of times greater than that of the induction gears as the number of sides of the cylinder
• the number of sides of the cylinder will be comparable to the magnitude of l internal gear divided by that of the induction gear.
• a retroactive two-sided blade motor like a post-active four-sided blade, will both operate in a three-sided, therefore triangular, cylinder.
• two machines, one retroactive and the other post active having for example the same number of sides of blades, or three, will both evolve in totally different universes, are a cylinder of four sides for the retro machine active, and two for the post active machine.
• the gears must be determined in order to accomplish these shapes.
• the induction gears must be equivalent to one on the number of sides of the cylinder, compared to the master gear.
• the induction gears must be one in three of the master gear.
• the ratio of the induction gears to the master gears must be equivalent to one on the number of sides of the blade.
• the induction gears will be one in two of the master gears.
• Complementary poly inductive supports applicable to poly turbines we present new realizations of poly inductive mechanics, which allow the more adequate support of the parts of poly inductive machines of poly turbine types.
• gears allow us, if we use non-sliding attachment points, only a passage between the rectangles and the diamonds.
• the second mechanism it succeeds in effect in reproducing the square shape that the tips of the blades performs over time, which from the external point of view does not appear as a square, but rather as a series of arcs of circles. going by accelerating and decelerating.
• a first way of solving the problem posed by the use of post rotary semi transmission, and of correcting, without the use of flexible blades, the support of the palic structure will be to organize the support of the blades differently. Here, on the contrary, it will not be according to their shape that we will decide where to attach the blades, but according to their angle.
• the blades will be attached to two support rods so that the end of the rectangle made by the palic structure will be in a rhombus, and when the rhombus of the gear structure passes, 90 degrees fanges of this will allow attachment to the square structure of the square.
• Figure VE shows that by considering things no longer from the point of view of a fixed external observer, but rather that of an external observer being itself in rotation by half the speed of the pale structure, we can understand that the static formation of a rhombus is equivalent to the formation of a square over time. Indeed, the square described by the tips of the blades only appears as such for an observer who, considering the structure in rotation , would itself be in rotation at a speed two times lower than that of the palic structure, as shown in the following diagrams in Figure V
• a first solution will consist in using a blade wedge support by a connecting rod subjected to the combined action of a crankshaft and a directional blade support rotating in opposite directions.
• Figure XVII E will show how to use the machine as a conventional two-stroke or, with the help of two structures, of the backflow type
• the blades will be nested in drive means such as crankpins or induction cams so as to produce differential fluctuations in the torques and counter-torques.
• the blades will be assembled in such a way as to capture the differential energy of these systems in order to actuate it in rotation. This action is all the more effective as the thrust is indeed given in the direction of rotation of the engine, which guarantees maximum torque.
• the object of the present invention is to show how these thrust effects can be obtained mainly and even strictly by the movement of driving parts one against them, the cylinder being able to participate or not simply passively in the retention of compression but not to the production of the torque generated by the thrust. This means that the engine could, at the limit, be started without a cylinder.
• the expansion and reduction of the combustion chambers will be caused by the approximation and the distance of the blades over time, in a cylinder of cylindrical shape.
• the movement of these blades is a combination of their own reciprocating movement and the circular movement of the entire system. This is why, apart from time, their movement is circular, but taking time into account, we can say that it is almost circular.
• a crankshaft is rotatably mounted on the body of the machine at the center of the support gear, which is of course and as we have already mentioned, perforated for this purpose.
• On the crankpin of this crankshaft is rotatably disposed a gear, the induction gear, so that it is coupled to the support gear. Therefore, the rotation of the crankshaft around its axis will cause, in the same direction, that of the induction gear. It will then be assumed that a crankpin, or else a cam is rigidly disposed on the induction gear.
• each blade will in fact be provided with preferably two runners, one on each side of the center. It should be noted that the system would also be functional with a single slide as an attachment point. These slides will each be engaged with an induction cam of the polyinductive semi-transmission.
• a polyinductive bridge type transmission will preferably be used. To do this, a master gear will be rigidly disposed in the side of the motor. A support membrane, rigidly connected to the central axis, will be rigidly provided with four rods supporting the induction gears.
• An induction gear fitted with a cam will be rotatably mounted on each connecting rod.
• the blades will then, while remaining threaded to the central axis and nested one to the other, coupled to their respective cams by the use of their respective slides.
• a complementary wall can then be fixed to the support rods, and will be well supported on a bearing located behind the master or support gear. Specific bearings with a flat exterior can absorb wear on the runners of the blades.
• a second arrangement (fig. XLX F), will keep only two blades. This time, the gears will be mounted as follows. We will first position two gears at their closest points (or distant), and on a parallel of the two complementary gears. the system will then be rotated in such a way as to position the next gear. And so also for the last gear.
• the distance between the blades can be caused in other more mechanical ways. For example, by using a central cross cam, or by using an external cam receiving a vertical thrust. (Fig. X ⁇ F)
• Figure XVI F represents a version rather using an internal type of support gear to effect the blocking of the other blade, this time effecting its advance by lever, which increases the power of the motor by increasing the force necessary for the dynamic and reducing the force required to block
• Figure XVHI F has the originality of producing a differential force, while uniting the two blades, the cams of each of which are of different sizes. Even thrust on both blades, even disregarding the blocking effects already discussed, will cause a torque differential which will push the system in a specific direction. The force produced between the two blades will have a stronger power on one than on the other, which will lead to the deconstruction of the system mainly on one side.
• Such a machine can be used as a pump, motor, etc.
• the use of internal type support gear will be preferable.
• spacing approximations may, by modifying the gear ratios, be produced several times per revolution for each blade, which will lead to several explosions per revolution per blade.
• the spacings and approximation will however be less accentuated.
• the originality of the differential motor lies largely in the fact that by causing a contradiction, a dynamic and mechanical backstop, the support can therefore be made, even in a rotary system, from one piece against the other, namely the active part against that located in the stop position. It is this originality that makes it possible to use a perfectly circular cylinder, because it only serves passively, to keep the compression of the gases.
• the present turbine therefore represents in our eyes an ideal in terms of motorology, since it succeeds in obtaining a thrust in the same direction of the rotation of the motor, and this by dividing and reducing the idle time of the motors by two, and finally by achieving movement through the use of internal gears, which well used, are synonymous with lever forces.
• this turbine also meets an ideal of reducing accelerations and decelerations outside systems requiring energy. It also meets an ideal because it is achievable in a backflow-proof manner, therefore clean.
• Such a turbine is also ideal in its weight-to-power ratio. It provides enormous power relative to its size. Lately, the double complementary action of the crankshafts, which recalls the symbol of infinity, which we have long wanted to apply in motorology, gives this structure an almost philosophical character.
• the present turbine represents an ideal of fluidity and speed. Although the speed of this one will be lower than that of a open turbine, it will be much higher than that of conventional engines, whether piston or anti or post rotary.
• Figure I A gives some examples of a poly induction motor. We can see the imbalance caused by the fact that the gear parts are located only on one side of the blade.
• Figure II A shows a transverse view of the semi-transmission where it is possible to highlight the locations of incomplete support and conducive to premature wear.
• Figure Hl A shows a first solution, more difficult to achieve, by the use of two complementary systems linked together.
• FIG. IV A is a first incomplete configuration of a semi-transmission of the bridge type, comprising for the moment only the bridge itself.
• the latter crossed by a central axis, is well supported on each side, by well supported bearings.
• an additional bearing can be inserted from the side of the bridge itself supported on the side of the engine.
• Figure VA shows the adaptations that will be made to the induction gears, which will however produce the same effect of power and geometry
• Figure VI A shows a more complete semi-bridge transmission and application to which the first gears, namely central and induction, have been added.
• the cams which will activate the connecting rods, blades or ink parts of the core of semi turbines, or other parts of motorizations which one will have chosen, according to whether one intends to build a piston engine, post or anti-rotary type, or even quasi-turbine type. or differential induction.
• Figure VU A shows a design of the semi transmission inserted in the blade itself.
• Figure XVIII A shows a semi transmissions leaving the center clear.
• the central axis having to stop at this level, a second support will be placed on a neck arranged behind the support gear.
• An additional arm can be connected indirectly, via a blade collar, to the crankpin of a crankshaft which will convey the energy mechanically to the outside
• Figure XIX A shows a first use of this type of semi transmission of a bridge in an engine, here of the straight piston type.
• the stroke of the cam is defined so as to be very exactly the same length as that of the master crankshaft.
• the cam is connected to a connecting rod, itself provided at each end with a piston.
• a semi-transmittive piston engine but this time having the advantage of being adequately supported.
• Figure XA represents the application of the same features to a semi transmission is of the retro-rotary type and, again in a very balanced way, allows the development, here of a triangular type motor.
• the master gear here is of internal type
• the blade is here rigidly connected to the induction gear, and at the same time mounted around the support axis of the bridge.
• the induction gear is coupled to the internal type support gear, arranged in the side of the motor.
• Figure I B shows a first way of making a triangular motor, in a polyinductive manner, using two induction gears working in combination so as to activate the blade. This achievement is already used and commented on in our previous work on poly induction
• Figure II B shows that by using a reverse semi transmission, retro rotary motors can be produced by using two inductions, this time induced by their centers, namely an eccentric, and a gear. central induction.
• This figure also shows that the retro-rotary qualities are respected, that is to say the total use of the surface of the blade, and the leverage developed by pressing on the induction gear.
• Figure Ht B represents a diagram of the forces in force during rotary descent of the blade.
• Figure IV B is a three-dimensional view of the last embodiment
• Figure VB shows that this configuration fully achieves the qualities of retro rotary motors since we can, from this build an infinite number of motors, of course respecting a calibration of the gears adequate to the number of sides of the blades and cylinder faces that we want to obtain.
• Figure VI B shows a second embodiment of semi-transmission modifying both the direction of rotation of the axes and their speeds.
• Figure V ⁇ B shows the main shortcoming of the previous configuration, causing a deficiency in compression
• Figure VL ⁇ B proposes a new embodiment of the invention, from which the semi-transmission mechanics are subtracted, by proposing a poly induction distributed differently.
• the two dynamic points of the engine are now the center actuating the crankshaft, and the internal type induction gear, arranged on the center of the connecting rod, and around the crankpin and engaged with the internal support gear located in the side of the block.
• this figure therefore also shows the desired result of this operation, that is, the improvement in compression.
• this realization retains all the retroactive qualities are preserved through this new realization.
• FIG. IX B is a commentary to a diagram representing the forces present during the descent rotation of the blade.
• Figure XB shows that we can even compress this system by improving the design of the blades.
• Figure XI B shows that an infinite number of such motors can be produced and somewhat exposes the gear ratios, dimensions of cylinder blades to be observed.
• Figure I C shows an example of poly inductive motors, the first being of the retro rotary type and the second being of the post rotary type. It shows in particular that, for each of them, the use of reversing induction gears, compared to accelerating induction gears.
• Figure HT C shows three different specific ways of making retro rotary motors, taken from our request for this purpose.
• Figure IV C shows how the forces act on the blades, and that one succeeds in taming the retroactive forces so as to make them participate in the positive deconstruction of the system, without loss of energy, and even with leverage.
• Figure V C shows the achievements of the multi-rotary way of mounting a rotary port motor, and why it is so named.
• Figure VI C current configuration of mono inductive rotary motors leads to a domestication of the forces of the explosion very deficient compared to the expression with three poly inductive blades already commented
• the figure VU C prior to the next embodiments, explains the main differences between the retro-rotary and post-rotary engines in terms of the direction of rotation of the crankshaft relative to that of the blade, depending on whether they are coupled to the reversing or accelerating gears of the poly inductive device.
• Figure Vm C shows that it is impossible, directly, to apply the retro rotary effect to a post rotary motor
• Figure IX C shows a different way of analyzing the movement of the blade compared to that of the crankshaft, this time not considered from the point of view of an outside observer, but rather that of an observer who would be located on the crankshaft itself, and comments on the considerations that follow.
• Figure XI C shows a first embodiment of a post rotary motor mounted in a retro-rotary manner.
• Figure XII C shows that the forces in such an engine fully achieve the desired domestication of all the thrust forces of the blade and the domestication of the deconstruction of the system.
• Figure XHI C is a three-dimensional representation of Figure XI
• Figure XIV C is a different version of the invention where two different types of reversals were used, namely the combination of a semi transmission, on the one hand, and an internal gear coupling.
• -external gear on the other hand
• Figure XV C shows a use of an internal gear in the semi transmission
• the figure XVI C represents a combination allowing the entrenchment of the semi transmission, by the use of two internal gears engaged on the same pivot axis arranged on the sleeve of the crankshaft
• Figure XVII C is a three-dimensional representation of the previous one
• Figure XVHI C is a representation of the energy captured by such a configuration, which also respects the principles of retro-rotation
• Figure XIX C shows an off-center way of carrying out the invention, this way allowing the system to be overcompressed
• Figure XXI C shows a minimized way of carrying out the invention by the use of a single internal gear floatingly arranged in the machine
• Figure XXII C shows the energy distribution during the expansion of such a system
• Figure XXHI C is a three-dimensional view of the last achievement. Part D of the summary description of the figures
• FIG. I D shows two embodiments of a poly inductive motor with a blade, one retro-rotating with a triangular type cylinder and the other, post rotary, whose blade is square. Two different polyinductive mechanics are used, and clearly shows the retroactive aspect compared to the post active aspect.
• Figure II D shows several successive figures showing the side rule plus one applied to the rotary engines.
• the blade has a number of sides one less than that of the sides of the cylinder.
• Figure HT D shows several successive figures showing the rule minus one applied to post rotary engines. In each figure, the number of sides of the cylinder is one less than that of the blade.
• Figure IV D compares the two types of motors for a blade with the same number of sides
• Figure V D shows a comparison between these two types of machine or motors, this time for cylinders with the same number of sides, ie three.
• Figure VI D shows the borderline cases of convergence of these two rules, in particular, when the blade is a line, or the cylinder is itself a line.
• Figure I E shows two schematic figures of poly turbines, in which we have arranged the two main forms of mechanical support already commented on said request.
• FIG II E shows the main shortcomings of these two support systems.
• the figure HT E represents a first way of designing a structure avoiding the previous difficulties by conceptualizing the angles of the support structure differently compared to the angles of the palic structure, and moreover, by connecting them rather indirectly, pale the recourse to blades specifically fitted. As we can see, this solution allows us to have only two support locations
• Figure IV E comments on the geometric difficulty to be resolved in order to be able to provide support when the palic structure is attached by the tips of the triangles forming it, namely that of producing a rectangle in place of the square already described.
• the figure V E shows, how, by changing the point of observation one can conceive a rhombus to observe statically, like the dynamic expression of a square.
• Figure VI E shows how we can transform this conceptualization into a technical solution by making the support gear dynamic.
• Figure VU E schematically shows the forces obtained by applying the two present solutions
• Figure IX E shows a first way of making said poly turbine.
• Two drive rods for the palic structure are each connected to the crankpin of a crankshaft, at the same time as they are subjected to a directional support rotating in opposite directions.
• Figure X E is a three-dimensional view of the previous figure
• Figure XI E shows how to simplify this structure in a first way, by cutting out the parts more prone to friction by using only gears, here strictly of external types
• figure XII E shows how geometrically how to obtain a rhombus, or a flattened oval from internal gears
• Figure XHI E shows, starting from these geometric achievements, how to further simplify this structure by expressing Figure XII E this time with the help of internal type support gear. This time, the drive rods will be rigidly placed on induction gears this time coupled to internal type gears.
• Figure XIV E shows a version of the last three-dimensional realization
• Figure XVI E shows the use of such a machine as a two-stroke engine, standard and backdraft
• Figure XVH E shows three different ways of supporting the palic structure through the center or the corners.
• Figure b shows a structure from different gears supporting the parts.
• Figure XHI E shows how to complete the two gear systems (with internal support gear) located on each side of the turbine, with a continuous crankshaft, whose center pins will ensure the reach of the complementary locations of the palic structure
• Figure XIX E shows how to complete the two gear systems (with external type support gear) located on each side of the turbine, with a continuous crankshaft, whose center pins will ensure the range of the complementary locations of the palic structure Part F of the summary description of the figures
• FIG. I F represents a first way of effecting a mechanical blocking, this blocking subsequently serving to produce a fulcrum on which the dynamic blade will produce its thrust.
• Figure II F shows how a crankpin can be placed in the stop position, but this time using an internal type induction gear. We will explain later how this procedure increases the power of the turbine.
• Figure HT F shows a first arrangement of several sets of induction gears and cams around the same support gear.
• Figure IV F shows how this support is made, between two blades provided with drive slides, each being rotatably mounted around the center, so that their drive slide is engaged on the induction cam.
• Figure V F is a three-dimensional view of Figure IV F
• Figure VI F shows how the blocking time is somewhat behind the moment of maximum approach of the blades, which we will correct in the next figures.
• Figure Vu F shows a first way to correct this delay, namely by producing in assembly with three blades.
• Figure VL ⁇ F is a diagram of the two main positioning of the cams over time, for a set with three blades.
• Figure IX F shows the assembly technique for placing the gears in a two-blade system, so as to make profitable, as in the last three-blade system, the stop positions as soon as possible.
• Figure X F is a diagram of the positions occupied by the cam gears for one revolution of the machine or of the motor. It can be seen there that the ignition will be shifted each time the blades are brought together in a proportion of one eighth of a turn.
• Figure XI F shows that the rotation of the previous system can be canceled by the use of an internal gear. This will allow, if desired, to keep the spark plug and valves in the same place.
• Figure XH F shows that one could force the separation of the cams mechanically, either by an internal cam or by an external cam. This way of doing things could find application in an embodiment of the machine as a pump.
• Figure XHI F shows how the blades can be arranged differently. This time, instead of being rotatably mounted in the center, and slidably on the cam, they are slidably in the center, and rotatable on the cam.
• the shape of the cylinder can no longer be round, and we fall, for example here on an eight shape.
• Figure XVII F shows that the same blockages can be obtained by using internal gears as support gears.
• Figure XVHI F shows a simplified embodiment of the invention where only one of the blades is active, the other being rigidly connected to the crankshaft.
• one of the blades is connected to the induction gear by its cam, and connected to the other blade by a connecting rod, which is also mounted on this cam.
• Figure XVHI F shows a way to increase the differential character of the previous ones.
• each blade is provided with an induction gear and a cam, but with the particularity that each of these cams is of different size.
• the action of the gear is therefore increased on one of the two blades, which causes an increased differential effect.
• This procedure however limits the number of explosions, because the blades can only use one of their sides as an explosion surface.
• Figure XIX F shows how the blades can be staggered to produce a backdraft version of the motor.
• This staging can also be used to produce, in the same engine, a staging of power .
• Anti-flow motors can also be constructed by dividing the chambers transversely by a wall.
• Figure XX F shows how the circulation of gases takes place in a conventional two-stroke version of the engine
• Figure XXI F shows, since it is possible in such an engine, to subtract the passive cylinder by a closed blade containing the other, how one can produce a mechanical wheel motor. Given the almost unlimited speed of such an engine, only a clutch would be required.
• Figure I A gives some examples of a poly induction motor. , using poly inductive semi transmission.
• a triangular retro-rotary motor 1 octagonal rotary rotary motor 2 and a straight piston 3, or quasi-turbines. All these kinds of engines use the type of semi-transmission mentioned above.
• Figure H A shows a transverse view of the semi transmission 4 where it is possible to highlight the incomplete support points
• Figure Ht A shows a first solution, more difficult to achieve, by the use of two complementary systems linked together
• a semi transmission 4 which allows the central crankpin and other parts to be supported more upright. It is however necessary to ensure equality of work of the two semi transmissions by connecting them by a means such as gears 6 to each other, by the use of an axis 7 itself provided with gears.
• FIG. IV A is a first incomplete configuration of a semi-transmission of the bridge type, comprising for the moment only the bridge itself 8.
• the latter provided with a central axis 9, is well supported on each side, by well supported bearings 10 on the body of the engine.
• Figure V A shows the adaptations that will be made to the induction gears, which will however produce the same effect of power and geometry.
• the induction gears 11, rather than being provided with a central gear axis, mounted on the crankshaft sleeve 12 and provided with a crank pin 14, will be provided with a cam 15 and rotatably mounted on the one of the axes 17 of the bridge
• FIG. VI A represents a more complete semi-bridge transmission and application, to which the first gears, namely of induction 11 and of support 17, have been added.
• the cams which will activate the connecting rods, blades or other parts of the semiturbine core, or other parts of motorizations which one will have chosen, according to whether one intends to build a piston engine, of post or non-rotating type, or of quasi turbine type, the cams will be connected to a blade 18, which will be inserted in the cylinder 19 of the engine 20
• Figure VH A shows a design of the semi transmission inserted into the blade itself.
• Figure XVHI A shows a semi transmission leaving the center clear.
• the central axis having to stop at this level, a second support will be placed on a neck arranged behind the support gear.
• we can before placing the center gear slide the support arm 22 on the gear neck 23.
• We can then rigidly arrange the support gear 17 We can also use an opposite method, by assembling this arm around the neck instead. Then the same applies for the second litter.
• This or the blade must be made in two pieces, so as to connect them.
• a second wrist 30 can be placed indirectly on the crankpin of the crankshaft and by the use of the latter 31 again driving the energy outward.
• Figure XIX A shows a first use of this type of semi-transmission of a bridge in an engine, here of the blade type and rounded cylinder.
• the stroke of the blade would prevent the central axis from passing through the engine.
• the blade 18 and its induction gear 11 are rotatably mounted on the crank pin of the bridge so as to couple the induction gear to the support gear 17.
• a neck can be arranged between the induction gear and the connecting rod, which we will call the connecting rod neck 33, to which a second crankshaft 34 could be, by its attached sleeve 35
• Figure XA represents the application of the same features to a semi transmission is of the retro-rotary type and, again in a very balanced way, allows the development, here of a triangular type motor.
• the master gear here is of the internal type. Note that, while not using an external gear support gear here, the center being cleared, the crankshaft can continue on this side 36 without an additional arm as in the previous figure
• the blade is here rigidly connected to the induction gear, and at the same time mounted around the support axis of the bridge.
• the induction gear is coupled to the master or support gear of the internal type, arranged in the side of the motor.
• Figure I B shows a first way of making a triangular motor in a poly inductive manner, using two induction gears working in combination so as to activate the blade. This achievement is already used and commented on in our previous work on poly induction.
• crankshaft 2 In the side of the machine 1 is first of all rotatably disposed a crankshaft 2 provided here with two crankshaft sleeves 3 at the ends of which gears are rotatably connected, which have been called induction gears 4. These gears are mounted so as to be coupled 5 each to the support gear 6, an internal type gear rigidly disposed in the side of the machine
• crank pins 7 or cams are then rigidly disposed on the induction gears.
• the blade 13 is then both connected to these crankpins and arranged semi-rotationally in the cylinder 8 of the machine.
• the action of the crankshaft clockwise 9, will cause, since they are both engaged to the support gear 6, the retro action of the induction gears 10 supporting the blade 13 by their respective crankpins.
• the calibration of the gears here being one in three, the blade 13 will turn in the opposite direction 11 of the crankshaft and will traverse the triangular figure of the cylinder, specific to the triangular engine 12.
• Figure H B shows that by using an invertive semi-transmission 14, retro rotary motors can be produced.
• two inductions this time induced by their centers, namely an eccentric, and a central induction gear, we can produce the same forms of movement of the blades as those of the retro motors.
• rotary This figure also shows that the retro-rotating qualities are respected, ie the total use of the surface of the blade, and the leverage developed by pressing on the induction gear.
• a pivoting reversing gear 21 will then be rotatably arranged in the side of the semi-transmission, so as to be coupled with the semitransmittive crankshaft gear 19.
• a third semi-transmission gear 22 is rigidly fixed to an axis which will cross the machine and the central axis of the crankshaft 19 over its entire width, to constitute the main axis 23. To this main axis, will be rigidly fixed a blade induction gear 24.
• the logic of the system resides in the fact that the blade must rotate at the same speed but in an inverted manner as that of the eccentric
• the induction gear since it is imbricated with an internal gear of twice its size must therefore, turn in reverse twice as fast as the free crankshaft to be able to actuate the gear of the blade to the same speed as that of the crankshaft. This explains why, the semi transmission not only reverses the speeds here, but also doubles them.
• the operation of the machine is as follows.
• the main axis of the motor turns, 25, it automatically drives with it the induction gears 22 and semi-transmission gears 22 to which it is rigidly connected.
• the induction gear drives the blade 13 in the same direction 28.
• the pivot gear 21 reverses the rotation of the axis gear and subjects the semi-transmission gear of the free crankshaft and its eccentric to a rotation, in the opposite direction to that of the blade 29
• Figure Ht B shows the commented system during the descent phase. This shows how the thrust on the blade will be all of a first part transmitted to the main axis, directly by pressure on the induction gear 30 to which it is rigidly connected. Then, the free crankshaft undergoing reverse thrust, and in addition from the reverse part of the blade 31, will induce the gears of the semi-transmission so that this force is rehabilitated in the right direction, namely that of the initial turning of the central axis 32.
• the retro-rotating forces are therefore domesticated to participate and even in a stronger relation to the rotary forces.
• Figure IV B is a three-dimensional view of the previous embodiment. We find all the elements already commented on.
• Figure VB shows that this configuration fully achieves the qualities of the rotary motors since one can, from this build an infinite number of motors, of course respecting a gear calibration adequate to the number of sides of the blades and cylinder faces that we want to obtain.
• the gears must be modified so that the free crankshaft completes the action of the blade. In an embodiment with a triangular blade for example, it must travel an active quarter turn 33 for an eighth retroactive dice turn of the blade 34. In a four-sided blade assembly, the crankshaft must rotate by 60 degrees active35 for the blade 30.
• Figure VI B shows a second way of producing an inverting semi transmission as well as a multiplier.
• the axis of the free crankshaft is terminated by a gear of the internal semi-transmission type 100, turning for example clockwise 101.
• the semi-transmission gear of the axis central it will be terminated by an external type gear 103.
• the two semi gears transmission will be connected to each other indirectly since they will both be coupled to the reversing pivot and reduction gear 107. Therefore the pivot gear will rotate in the same direction as the axis of crankshaft 105 and will reverse the direction of the central axis by multiplying it 106.
• Figure VU B shows the main shortcoming of the previous configuration, causing a deficiency in compression. Indeed we see that the ratio is about 1 to 3.5, 37
• the objective, to correct the shape of this cylinder would be on the one hand that the blade goes deeper into the side of the cylinder during compression 38 and more that the side of the cylinder is less curved 38 b, it is ie kept closer to the blade.
• Figure VLH B proposes a new embodiment of the invention, to which we subtract the semi-transmission mechanics, by proposing a poly induction and which would solve the objectives previously mentioned.
• crankshaft 40 is provided with a standard crankpin instead of an eccentric.
• this crank pin 40 b is rotatably disposed the blade 13, as well as the induction gear 14 with which it is provided.
• This induction gear is then coupled to an internal type support gear 6, here three times the size, placed in the blanks of the block 1.
• Figure IX B shows the operation of this machine, which in the form of an engine is as follows.
• the explosion we have, as in almost any engine, a neutral position. Indeed, since the induction gear 14 and the crankshafts 40 are centered, the thrust is also distributed on the blade. But the importance is above all to check what happens during the deconstruction of the system.
• FIG. XB shows that we can even compress this system by improving the design 200 of the blades. Indeed, by pushing the last technique to its limit, the blades will go so far into the cylinder that it will be necessary to cut them in a way more adapted to the curvature of the cylinder, itself designed according to the travel of the ends of the blade.
• Figure XI B shows that an infinite number of such motors can be produced.
• Figure I C shows an example of poly inductive motors, the first being of the retro-rotary type and the second being of the post-rotary type. It shows in particular that, for each of them, the use of reversing induction gears, compared to accelerating induction gears.
• crankshaft 1 provided with two opposite sleeves 2 is rotatably mounted in the body of the machine 3.
• the first support gear is internal type 4a and the second external type 4b.
• gears which will be called induction gears 5, so as to be coupled to the support or support gears.
• the induction gears 5 will be provided with crank pins 6 or cam, to which the blade 7 will be connected
• figure HC we reproduce the figure representing the generalization of these engines, and which indicates the similarities and geometrical differences of these two categories.
• two infinite series of motors can be produced by following the story rule which says that for all poly rotary rotary motors the number of sides of the blades is one less than that of cylinder 7, while for post rotary engines, the number of sides of the blade is one greater than that of cylinder 8
• Figure HT C shows three different specific ways of making retro rotary motors, taken from our request for this purpose titled Semi transmittive assembly of semi transmittive induction motors. In one 9, one acts as previously described. In the second with the help of a semi transmission 10, and thirdly with a direct retro-centric mounting 11.
• the figure IV C shows how, for example for the second figure, the forces act on the whole blade since one succeeded in taming the retroactive forces so as to make them take part in the positive deconstruction of the system, without loss of energy , and even with leverage.
• the forces on the blade directly force, on the left 12 the displacement of the crankshaft downwards 13, while these same forces act on the induction gear coupled to the blade gear 14 by turning it to the right 15, in the opposite direction to the crankshaft.
• this movement is reversed by semi-transmission and retransmitted in the right direction to the crankshaft 1.
• the crankshaft is therefore subject to the addition of forces.
• Figure VC shows what has been learned in the multirotative way of mounting a post rotary engine, and why it is so named. Without being as powerful as the retro-rotary, this way of doing is still advantageous in that it has the capacity, even if it does not domestic them for all that, to cancel the effects of retro rotation of the engine.
• the thrust 17 on the crankpin of the induction gear 5 is automatically countered by a counter-thrust 18 of the crankpin of the crankshaft 1. All the thrust 19 on the rear part of the blade is not effective, but also not harmful, which allows the total use of the remaining part of the blade.
• the thrust this party is carried out on a crank pin whose decentering and acceleration towards the outside 21 has increased the torque.
• This motor is therefore more powerful than a motor, for example rotary, with simple dynamic induction as we will show in the next figure
• a first difficulty with this type of motor is that the thrust on the rear part of the triangular blade of the motor 22 produces a counter-thrust on the blade, contrary to the direction of rotation of the motor. Not only is almost a third of the energy thus lost, but it is necessary to allocate more than the second third and a half of the central part of the blade 24, awaiting the additional effect of lever to counter, to cancel this rear pressure . There is therefore barely 25% of the energy available positively, and moreover, as we will show, fairly reduced energy. Indeed, for this remaining quarter, we must count a low torque 25 , since the face of the blade tends to follow, although at reduced speed, the movement of the crankshaft.
• Figure VHI C shows that it is impossible, directly, to apply the retro-rotary effect to a post rotary motor.
• a blade on three sides.
• Figure IX C shows a different way of analyzing the movement of the blade compared to that of the crankshaft, this time not considered from the point of view of an outside observer, but rather that of an observer who would be located on the crankshaft itself, and comments on the considerations that follow. Indeed, assuming that our observation point, rather than that of an external observer, is that of someone located on the crankshaft 34, the observer would see, after a quarter turn of rotation of that -this, that its reference point located on the side of the engine would have moved to its left by 90 degrees 35, but, what is more important for the present, that the blade will have moved to its left, that is i.e. the rear, 45 degrees 36. This means that the vale is active with respect to the engine body, but on the other hand, retroactive with respect to the crankshaft
• Figure XI C shows a first embodiment of a post rotary motor mounted in a retro-rotary manner.
• the basis is as follows. We know that the action of the blade is retroactive, not in relation to the engine, but in relation to the crankshaft. We will therefore act by supposing first of all a crankshaft without any eccentric which will be arranged rotatably in the engine, this crankshaft being able to serve at the same time as central axis of the engine. rotatably mounted 40.
• a secondary crankshaft 41 provided with an eccentric as well as, in its side, a wedge gear 42 will be arranged around the axis so that its gear is coupled to the pivot gear 40.
• a second gear 43 On the central axis, a second gear 43 will be coated rotatably so that it is moreover connected to the pivot gear 44. To this induction gear, will be rigidly connected a spur gear 45, which will in turn be coupled to the internal mesh of the blade.
• a blade 7, provided in its side with an internal gear will be rotatably mounted on the eccentric of the crankshaft in such a way that the internal gear with which it is provided is engaged with the induction gear of the reverser.
• crankshaft a second gear 47, which will be coupled to the reversing gear of the semi-transmission 48.
• This latter gear will be placed in rotation in the block of the semi-transmission 49.
• a third semi-transmission gear 50 will be rigidly disposed on the central axis so as to be coupled to the reversing gear.
• Figure XH C shows that the forces in such an engine fully achieve the desired domestication of all the thrust forces of the blade and the domestication of the deconstruction of the system.
• the rear thrust in feedback 51, actuates the free gear mounted on the axis 52, which in turn actuates the internal pivot gear of crankshaft 53 which in turn actuates l crankshaft gear 54.
• crankshaft 55 On another side the blade acts on crankshaft 55, making it rotate in the same direction as before. The rotation is then subjected to the semi-transmission gear outside of the crankshaft is then transferred and reversed by the semi-transmission pivot gear 56, which then induces the axis transmission gear, which retransmits, in a single energy, the cumulation of the thrusts outwards, but, this time in the opposite direction of the crankshaft.
• the motor is therefore indeed retro-rotating, its blade acting by accepting all the thrusts as much as counter-thrusts, and its output axis being in the opposite direction to that.
• This mechanism definitely provides more power than the conventionally used mechanics, and this mainly because it cancels the power losses already discussed, in addition to producing positive leverage effects.
• Figure XHI C is a three-dimensional representation of Figure XI
• FIG. XIV C is a different version of the invention where two different types of reversals have been used, namely the combination of a semi-transmission, on the one hand, and a gear coupling. internal - external gear on the other hand.
• crankshaft 1 fitted with an eccentric will be inserted in a block.
• it will be a free crankshaft, in the sense that it will not be it that will bring the energy to the outside.
• One end of this crankshaft will end in the semi-transmission, and will be rigidly connected to a semi-transmission gear 60.
• a blade 7, provided with an internal gear in its side, will be inserted in the cylinder of the machine 61 so as to be rotatably mounted on the eccentric of the crankshaft, at the same time as its gear will be coupled to the gear d induction of the central axis 48.
• a reversing pivot gear 49 will be rotatably disposed in the side of the semi-transmission so as to be coupled to the crankshaft and central axis gears of the engine.
• a central axis of the engine passing through the crankshaft and provided respectively at each end with a transmission gear 5 and at the other with a blade induction gear 5, will be rotatably inserted in the engine, so that its gear transmission is coupled to the pivot transmission gear, and its induction gear is coupled to the internal gear of the blade.
• Figure XV C shows a use of an internal gear in the semi transmission. Indeed, here, instead of, as previously, using a gear that is both reverse and reduction, we can separate the functions, and use a pivot gear to which we will attribute only balancing functions, the inversion being produced with the use of an internal mesh.
• the end of the crankshaft coupled to an internal type transmission gear 48 will be assumed.
• This gear will be coupled to the pivot gear 49, which having received the reverse movement of the internal gear, will transmit it to the gear of the central axis 50.
• the whole will be attached to a structure such as in XV for an identical result.
• the figure XVHI C represents a combination allowing the entrenchment of the semi transmission, by the use of two internal gears. engaged on the same pivot axis disposed on the crankshaft sleeve. Indeed, the last structures will have shown us that the inversion by internal gear taking months of pieces. This figure even shows that one could dispense with the use of a semi transmission. Indeed, here we will have rotatably on the eccentric of the crankshaft of the machine, at the height for example, an axis 80 provided. at each of its ends an induction gear 81, 82. Care should be taken to calibrate the gears so that the incidence of the induction gear is less pronounced on the rod of the desired degree, depending on whether a square, octagonal, etc. motor is to be produced.
• One of the gears will be coupled to an internal gear disposed in the side of the block 83, while the second will be arranged so as to be coupled to the internal gear of the connecting rod 84.
• Figure XXI C shows an off-center way of carrying out the invention, this way allowing the system to be overcompressed.
• the internal meshes will be coupled differently to the axis of the crankpin.
• Figure XXH C shows a configuration of the blade obtained by the previous embodiment 102
• Figure XXHI C shows a minimized way of carrying out the invention by the use of a single internal gear floatingly arranged in the machine. It is of primary importance, in motorology, after we have discovered a new way to positively solve and solve a problem, to see to realize it in its simplest expression,
• Figure XIV C shows the energy distribution during the expansion of such a system.
• the external gears must be of equal size, and this must be half the size of that of the internal gear.
• the post active thrust 121 of the blade will be transferred to the eccentric of the crankshaft 122. Furthermore, the retroactive thrust on the blade 123 clinging to the internal gear 124, itself clinging to the meshing of support 125, will act as a leverage 126 on the crankpin of the crankshaft, causing it in the same direction as that of the post-active sticky. Once again, take place to be subtracted, will the forces not only be added but multiplied.
• This retroactive version is almost four hundred times more powerful than the mono inductive version.
• Figure XV C is a three-dimensional view of the last achievement
• Figure ID represents two different versions of a poly induction motor, the first being of retro rotary type, with triangular cylinder, and the second, being of post rotary type, and here, with square blade.
• two induction gears 2 are coupled to an internal type support gear 3, and thus activate the blade 5 by their crankpins and, in the opposite direction 5, the crankshaft 6.
• the induction gears 2 are rather coupled to an external type support gear. By their crankpins, the induction gears therefore activate the blade 7 and, at the same time the crankshaft and its crankpin, this time in the same direction as that of the blade 8
• Figure H D represents a series of retro-rotary machines, which show a whole version of the blade ruler plus one. Indeed, as can be seen, the figure whose blade has two sides 9 has a cylinder with three sides. The figure whose blade has three sides 10 has a cylinder with four sides. The figure whose blade has four sides 11 evolves in a cylinder with five sides. And so on ad infinitum.
• Figure IH D shows a set of figures corroborating the dimensioned blade minus one rule for the post-rotary machine.
• the first represents a figure of a post-rotary machine whose blade has a number of sides of one greater than the cylinder.
• a two-sided blade indeed evolves in a 12-sided cylinder.
• a three-sided blade evolves in a cylinder; two-sided 14.
• Figure IV D compares the two generations of motors, starting from the idea that each one has a two-sided blade
• the cylinder is on three sides 15 while for the same blade, the cylinder of the post rotary machine is on one side, of course in the broad sense of the word, since is here, in this boundary figure, completely folded in on itself 16
• Figure V D is rather a comparison of these two generations of machines, starting from the idea that they would both be built with a triangular type cylinder.
• the blade has two sides 17, while for the post rotary motor, it will have four sides 18
• Figure VI D shows, in their simplest poly inductive version, the qualification of the induction gears in relation to the support gear to arrive at the desired number of cylinder sides
• the size of the support gear 19, (here 3), divided by the size of the induction gear 20 (here 1) is equal to the number of sides of the cylinder, so here three 21
• the size of the support gear 22 (here 2), divided by that of the induction gear 23 (here 1) is equal to the number of blade sides 24 (here 2)
• Figure V D shows the limiting moments of this rule.
• the blade ideally is only a point
• the cylinder is a line .25. This is what happens with straight rod motors.
• a second limiting example is when there is almost identity between the retro and post inductive machines. Indeed, a retroinductive machine with a blade on one side results in a cylinder shape in double arcs 26 similar to that of a post rotary machine with a two-sided blade evolving in a cylinder with one arc side 27.
• Figure I E shows two schematic figures of poly turbines, in which we have arranged the two main forms of mechanical support already commented on said request.
• a palic structure 1 formed of four blades 2 connected to each other by their end 3, and thus inserted into the cylinder 4 of the machine 5
• a support structure composed of two induction gears 6 provided with crank pins or cams 9, are each rotatably mounted on a crankshaft sleeve 7 and coupled to an external type support gear 8.
• Connecting rods 10 connect the cams to the complementary point of attachment of the blades 11.
• induction gears 6 are rather connected to an internal type support gear 13.
• the connecting rods this time link the cams 9 to the center of the blades.
• Figure HE shows the main shortcomings of these two support systems.
• the structure of the gears in its successive times, varies between the shape of a rhombus and that rectangle .14
• This structure is unfavorable since it forces two convolutions of the palic structure different, depending on whether the square is supported by the right or by the left 15.
• the main difficulty lies in the idea that the shape described by the cam of the gears is square 16 while that required is of the rhombus or flattened oval type 17
• Figure IH E represents a first way of designing a structure avoiding the previous difficulties by conceptualizing the angels of the support structures differently from the angles of the palic structure, and moreover, by connecting them rather indirectly, by using recourse to blades specifically fitted. As we can see, in this solution allows us to have only two support points
• two intermediate connecting rods for supporting the palic structure provided with drive slides 19 are rotatably mounted on the axis of the machine 18 so that their slides are engaged 20 on the induction gears 6.
• each of the ends of these connecting rods will be connected to a centered location of the blades 21.
• the operation of the machine will be as follows. Since the slides will cancel the vertical aspect of the movement of the cams, a right angle will be formed between it when the cams are complementarily placed in pairs, respectively at their most closed position and at their most open position 22. From then on, the palic structure will be in a square position.
• the induction cams will be found, consecutively, each closer 24 and farthest 25 from the previous and next cam. Therefore the palic structure will have the desired diamond shape 26
• Figure IV E comments on the geometric difficulty to be resolved in order to be able to provide support when the structure is attached. palic by the tips of the triangles forming it, namely that of producing a rectangle in place of the square already described. It should be noted that the structure, to effectively support the parts, with the help of an internal type of support gear, must travel in the shape of a rectangle.
• the figure V E shows, how, by changing the point of observation, one can conceive a rhombus to observe statically, like the dynamic expression of a square. Indeed, that We supposed to be able to observe the displacement of the parts starting from a reference point placed in the center of the system, but pivoting on itself at a speed of two times lower than that of the system, one could note that the formation of a rhombus, is that, dynamically of a delayed square.
• the point al represents a given point of the cylinder chamber, and the point b 1, a given point of one of the blades of the palic structure.
• the following representations show the displacement of the palic structure and of the pre-described point from the point of view of a moving observer, which leads, from the point of view of F observers, to the formation of the square to be produced 102.
• Figure VI E shows how we can transform this conceptualization into a technical solution by making the support gear dynamic. It will be enough to produce a semi reverse transmission 300, such as for example those which we show on our retro and post rotary motors so as to induce the support gear in the opposite direction to that of the induction gear, here in a report one eighth of a turn for the support gear per half turn of the induction gear.
• the support gear 8, the end of which this time will be terminated by a semi-transmission gear 60 can be rotatably mounted in the machine 61, so as to be coupled to a pivot and reducing gear .62, this gear will in turn be coupled to a transmission gear arranged on the crankshaft 63, which at its opposite end will support the induction gears 6, of which the cams 9 will support the blades 2 L 'It will be noted that four cams 9 will be used to remove any autonomy from the palic structure.
• Figure VH E schematically shows that the forces obtained by applying the two present solutions are retroactive. Indeed, the forces 65 on the blade will act on the crankshaft of the induction gears 66. On the other hand, the forces applied to the induction gears themselves will force the action of these 67, which, reversed by the semi transmission, will be positively transformed on the crankshaft and will be added to it 68.
• Figure VHI E shows that, as we have already mentioned, a support of the blades by their end could be sufficiently effected by only two attachment points 200, which would cut off part of the parts necessary for mounting the machine.
• Figure IX E shows a first way of achieving said way of doing things.
• Two drive rods for the palic structure are each connected to the crankpin of a crankshaft, at the same time as they are subjected to a directional support rotating in opposite directions.
• two connecting rods 10 will connect the crank pins 7 of a crankshaft and the opposite connection points of the palic structure 70.
• a rotary part for inducing the orientation of the connecting rods 201 will be rotatably disposed in the body of the machine, so that its movement 72 is the reverse of that of the crankshaft 73. This reversal could, as before, at the rate of one revolution for one, be carried out by a semi transmission connecting by a pivot gear the gears of the crankshaft and of the rotating part for orienting the connecting rods.
• the palic structure will be totally conditioned to the movement of the rods and will carry out the desired movement.
• Figure X E is a three-dimensional view of the previous one
• Figure XI E shows how to simplify this structure in a first way, by cutting off the parts more conducive to friction by using only gears, here strictly of external types Indeed, we will assume here that the connecting rods, connected to the palic structure are rigidly arranged on one of the induction gears 6.
• Figure b shows the movement of the parts for one revolution of the machine.
• a figure XH E shows how geometrically how to obtain a diamond, or a flattened oval from internal gears.
• the figure described by this point located outside its circumference is that of a rhombus, the shape we want, to involve the outer surface of the poly turbine.
• Figure XHI E shows, starting from these geometrical achievements, how to further simplify this structure by expressing figure XH E this time with the help of internal type support gears
• the gear support was active and in addition in the opposite direction of the crankshaft supporting the induction gears, we realize the cancellation of the friction found in the previous figure.
• the number of parts remains quite high, given the use of a semi transmission.
• Figure b schematically shows the movement of the parts for a quarter turn. This time, we will rigidly arrange the connecting rods drive on induction gears this time coupled to internal type gears
• Figure XIV E shows a version of the last three-dimensional realization
• Figure XV E shows the enormous forces developed by such a structure. Indeed we can first of all note that during the explosion, at the strongest moment of compression, the angle of attack of the crankshaft is 45 degrees 90 rather than zero in conventional engines. It will then be noted that the same explosion connecting the chambers 91, or even two simultaneous explosions will crush 92 the square of the palic structure, which will not have a pushing effect on the connecting rods but a pulling effect, much more powerful, attracting them outwards 92. Lately, it will be noted that these forces are not direct, but rather produced under the lever effect, activating the crankshaft resting on the internal support gear 93.
• Figure XVI E shows the use of such a machine as a two-stroke engine, standard and backdraft.
• the gas acceptance will be devolved to the part of the blade having a counter torque during its most compressed phase 100, which at this time will inject the new gases into the next chamber 110, thereby ejecting the used gases 111.
• the new new gases will be found, a quarter of a turn further, compressed and exploded, by the blades having improved torque, while the complementary blades will again accept new gas.
• backdraft machine one can use two blades, or even partitioned blades.
• Figure XVH E shows two different ways of achieving the support mechanism of the palic structure by the center or the sides.
• a master crankshaft 700 we show how to use a master crankshaft 700 to both receive 7001 the steering rods 702, and to support the crankpin induction 250, which, activated by the induction gears 703 and support 704, will check the opening rods 705 of the palic structure.
• Figure b shows how to achieve this structure from internal gears arranged in the blades.
• the induction gears and cams will be rotatably mounted on subsidiary crankshafts 115, which will be coupled to master induction gears 116, coupled to a main support gear 117.
• Figure XHI E shows how to complete the two gear systems (with internal-type support gear) located on each side of the turbine, with a continuous crankshaft 500, whose crank pins 501 will ensure the range of the complementary locations of the connecting rods complementary to the palic structure
• the crankshaft connecting the two semi-transmittive structures is provided with additional crank pins 500 to which are attached connecting rods 10, connected at their other end to the complementary attachment point of the palic structure.
• Figure XIX E shows how to complete the two gear systems (with external type support gear) 8 located on each side of the turbine, with a continuous crankshaft 500, of which crank pins of center 501 will ensure the range of the complementary locations of the palic structure. This way of doing things will make the explosion multiplied, the induction gear always serving as a pivot, even if the induction is more forward and backward alternately.
• Figure IF shows a first way of literally performing dynamic mechanical locking.
• a gear that we call support gear 2 This gear, provided in its center with a conduit 3 capable of receiving the central axis of a crankshaft 4.
• a crankshaft 5 whose central axis is rotatably inserted in this center of the machine, through the support gear.
• This crankshaft sleeve is itself provided a conduit 6 which can in turn receive the central axis of a gear 7, which we will call the induction gear 8.
• the length of the crankshaft arm will be determined and designed so that the induction gear is coupled to the main gear.
• the central axis of the induction gear is itself provided with an arm and a crankpin 10.
• the structure can also be mounted in the form of a cam, as we define more generally in our request for this purpose, but by way of representation, we think that the use of a crank pin will make the demonstration more clear and obvious.
• Figure H F shows that a similar type of blocking can be produced this time using an internal type support gear.
• crankpin is the upper part of its convolution when it is in the stop position. 10
• Figure IH F is a schematic view of the initial arrangement of the turbine gear parts.
• crank pins of the induction gears for cams 17.
• these will be connected two by two to the blades.
• the gears will be arranged so that two of them have their cams placed in their most distant position 18 while the two cams of the opposite complementary gears will be placed in their closest position 19.
• cams When the cams are placed in the blocking position, it will be said that they are a stopper, while the complementary cams are said to be dynamic.
• the figure TV F represents a semi-transmittive configuration similar and more complete than the previous one, to the previous one to which the blades 21 have been added.
• the blades will open up to their maximum, thereby closing the spaces located in their complementary sides
• Figure V F shows a three-dimensional view of the machine previously explained. in this machine, the two blades act against each other, the first serving as dynamic blocking allowing the thrust on the second to have a dynamic incidence
• Figure VI F shows the main shortcoming of the last achievements. It shows indeed that the moment when the blocking effect becomes effective is quite late after the ideal moment of the explosion, namely that of the maximum bringing together of parts, location that we have shown by dotted lines. It is indeed necessary to wait until the blocking system sees are cam exceed the perpendicular level 39 or the two opposing forces will begin to oppose before causing the explosion. This delay will cause a premature opening of the dynamic blade 41 and consequently a loss of compression since the blades will have started to distance themselves 40. If the explosion is anticipated, there will be an undesirable effect of recoil, and the differential force will decrease considerably.
• Figure VH F shows a first way to correct this by using a larger number of blades, which reduces the angles 43 between the cams and allows the dynamic cam not yet to start to come out, while the blocking cam enters in its blocking phase.
• the gears 8 and cams 17 of induction are six in number and the blades 21 three in number. It should be noted that not only can a greater number of blades be used, but also that several alternative movements per revolution can be determined for each, which will be capable of allowing continuous ignition.
• Figure VTH F shows the starting position of the six gears, the gears yl, y2 and zl, z2, being as close as possible, in pairs, to each other 51.
• the gears xl, x2 they are in their most prominent position in the system relative to the center 52.
• Figure IX F draws on the latest data to apply it to a system with two blades and four gears.
• the technique no longer aims to place the opposite cams in their closest or distant position, but rather to place the consecutive cams, successively in their position either the closest, or the most distant, depending on what one has chosen.
• Figure X F shows the eight main phases of this system. It will be noted that at each approach 54, the blocking and the dynamic thrust are maximum and that the approach of the cams is always done an eighth of a turn 46 before the previous one, in the opposite direction of the movement of the parts. Candles may be placed at each maximum location of the various blade approaches.
• Figure XI F shows that we can cancel the overall rotation of the system so that the points of approach of the blades are always done in the same places.
• crankshaft conduit so that it can influence the support gear by the use of a reduction gear 62, rotatably disposed in the block.
• the support gear 65 must be rotated in the side of the machine 1.
• This gear by its speed 63 of advancement will compensate for the recoil of the system and allow the closing of the cams always in the same place.
• Figure XH F shows how one could force the separation and removal of the induction cams by specific cams in the shape of a cross or clovers 72.
• Figure XHI F shows how we can improve the buffer 75 and dynamism 74 angles by tilting the blade slides a few degrees 73.
• this figure shows that the use of a specific pad 76, whose external shape is flat 77, will dampen the knock force on the blade
• Figure XIV F shows how the slide of each blade can be arranged differently. This time, instead of being rotatably mounted in the center, and slidably on the cam, they are slidably mounted in the center 81, and rotatably in the cam 81.
• the shape of the cylinder can no longer be round 83, and we fall, for example here on an eight shape. The action of the blades, one against the other, will remain differential. The shape obtained recalls that of an eight.
• part B of this figure the blades are rather towards the center, nested one with the other in a sliding way, which slightly modifies the shape of the eight which one will obtain. Note that by attaching a straight floating piece to the end of the blade, the shape of the cylinder will be an exaggerated eight, approaching the rectangle.
• Figure XV F modifies the rotary attachment points of the blade by assigning it to one of the two cams.
• each blade will be rotatably attached to one of the two cams 92, and in a sliding manner to the complementary cam 93.
• the force released by this arrangement will also be differential, but the shape of the cylinder will be rounded differently. Again, the differential action will be maintained, but here the dynamic point of the blade will be increased by lever.
• FIG. XVIF shows in a more complete manner a thrust obtained from a complementarity of buffer 29 and dynamic 30 actions, but this time by using internal gears as support gears.
• FIG. XVH F shows a simplified embodiment of the invention where only one of the blades is active, the other being rigidly connected to the crankshaft 102.
• one of the blades is connected to the induction gear by its cam, and connected to the other blade by a connecting rod 100, at a point lower or higher than the first attachment 101, so as to produce a differential force.
• Figure XVHI F shows a way to increase the differential character of the previous one.
• the two blades which directly joined by a system this cam.
• each blade 21 is provided with an induction gear and a cam 17, but with the particularity that each of these cams is of different size 105.
• the action of the gear is therefore increased on one of the two blades, which causes an increased differential effect.
• These chambers will be kept simply to admit or suck the gases.
• Figure XIX F shows how the blades can be staggered to produce a backdraft version of the motor, this time produced by stages 105 or partitions 107.
• This staging can also be used to produce, in the same engine, a staging of power.
• Anti-flow motors can also be built by assembling two sets. They can also be constructed by separating and partitioning the blades transversely, each blade opening possibly, at a given time, being concomitant with the other.
• Figure XX F shows how the circulation of gases takes place in a conventional two-stroke version of the two-blade engine. We find there the admission, the compression of the new gases, the exhaust filling, the compression towards the combustion.
• Figure XXI F shows how one blade can be used at a time as cylinder 200.
• the motor can be designed as a mechanical wheel motor.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Structures Of Non-Positive Displacement Pumps (AREA)
• Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

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• 2002
  • 2002-03-11 WO PCT/CA2002/000340 patent/WO2002075118A1/fr not_active Application Discontinuation
  • 2002-03-11 EP EP02708068A patent/EP1370748A1/de not_active Ceased
• 2005
  • 2005-11-21 US US11/282,732 patent/US20060073059A1/en not_active Abandoned

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