Rotary-piston engine

Abstract

The present invention relates to an engine or pump called rotary piston engine or pump, comprising a shape of revolution F relative to a delta axis, and rotatably movable about said delta axis in relation to an envelope V, and n cavities distributed over the perimeter of F. In each cavity is housed a rotating roller, characterized in that at least one roller has its center angle determined so as to obtain the closed volumes it delimits, as large as possible.

Claims

1. A rotary piston engine, comprising: a shape of revolution relative to a delta axis, and rotatably movable about the delta axis in relation to an envelope, a plurality of cavities which are shapes of revolution of a corresponding axis, distributed over a perimeter of the shape of revolution, a plurality of rollers each disposed in a corresponding one of the plurality of cavities, each roller of the plurality of rollers rotates about the corresponding axis and further includes at least a first face and a second face, wherein the first face is capable of ensuring sealing with at least one cavity of the plurality of cavities at some moments of a cycle of the engine when the first face is inside the at least one cavity and a section of each roller, as viewed in a plane perpendicular to the corresponding axis, is an arc of circle centered on the corresponding axis, with a center angle, a mechanical component configured to make the rotation of each roller of the plurality of rollers about the corresponding axis proportional to the relative rotation of the delta axis of the shape relative to the envelope, the envelope being defined by a first plurality of the plurality of rollers in their rotational motion about their corresponding axis, each driven by the shape of revolution and the relative rotation of the delta axis of the shape of revolution relative to the envelope, the second face ensuring sealing between each roller and the envelope, a section of the engine, when viewed in a plane perpendicular to the delta axis, the envelope, the shape of revolution and one of the ends of the arc of circle of the first face, are in contact, in a same location, at a particular moment of a cycle of the engine, side walls or a first flange and a second flange over which the shape of revolution, the roller, and the envelope bear, the shape, the rollers, the envelope, and the flanges, cooperatively delimiting volumes that are closed and variable at different moments of the cycle of the engine of the relative rotation of the shape of revolution relative to the envelope, the engine being wherein at least two cavities of the plurality of cavities are contiguous, and in that, between the at least two contiguous cavities, a passage is arranged so that, when a first end of the envelope is between the at least two contiguous cavities, a fluid that has been compressed by a first face of the first end of the envelope, can pass on a second face of the envelope.

2. The engine according to claim 1, wherein at least one roller of the plurality of rollers has a center angle determined so as to obtain the closed volumes it delimits.

3. The engine according to claim 2, wherein the center angle is lower than 180°.

4. The engine according to claim 1, wherein at least one roller of the plurality of rollers has a center angle determined so as to close the preceding volume, at the same time as it opens the next closed volume.

5. The engine according to claim 1, wherein the shape of revolution surrounds the envelope.

6. The engine according to claim 1, wherein the shape of revolution is surrounded by the envelope.

7. The engine according to claim 1, wherein the corresponding axes around which each of the plurality of rollers rotate are parallel to the delta axis and located at a same distance from the delta axis.

8. The engine according to claim 1, wherein the shape of revolution, each of the plurality of cavities, each of the plurality of rollers, and the envelope are cylindrical with generatrices parallel to the delta axis.

9. The engine according to claim 1, wherein the section of each roller of the plurality of rollers disposed along a plane passing through the corresponding axis defines a non-rectangular surface.

10. The engine according to claim 1, wherein an intake of fresh gases passes by the inside of a central rotary piston.

11. The engine according to claim 1, wherein an exhaust of burnt gases passes by the inside of a central rotary position.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The following figures and the descriptions of some particular implementations will allow a better understanding.

(2) FIGS. 1 to 23C cover embodiments according to the 1.sup.st implementation, that is to say, the shape F is in the outside, the envelope V is in the inside. The shape F is fixed, and the envelope V rotates. The envelope V is the central rotary piston.

(3) FIGS. 1 to 5 show different steps of the design of a first embodiment of an engine according to the invention allowing obtaining the geometric shapes of said engine.

(4) FIGS. 6 to 11 illustrate the different steps of an operating cycle of an engine according to the invention.

(5) FIGS. 12 to 16 show engines with rollers having different values of the center angle.

(6) FIG. 17 shows the value of the limit angle ω1 and the length OQ based on the value of the half-center angle of the rollers (μ).

(7) FIGS. 18A and 18B show a valveless engine.

(8) FIGS. 19 to 22 show some examples with different coefficients m and different values of the number of cavities.

(9) FIGS. 23A and 23B show an example of driving with gears. FIG. 23C shows non-rectangular sections of G_i.

(10) FIGS. 24 to 31B show a second embodiment of an engine according to the invention.

DETAILED DESCRIPTION

(11) In these examples, the axes β_i are parallel to delta and located at a same distance d from delta.

(12) The shape F and its cavities A_i, the rollers G_i, the envelope V are cylindrical with their generatrices parallel to delta. The side walls J1 and J2 are perpendicular to delta.

(13) In these conditions, it is preferable, in order to understand, to represent the system by a section BB by a plane perpendicular to the delta axis (FIG. 23).

(14) In order not to overload the writings on the drawings, regarding the 1.sup.st roller G_1, the point P_1, the cavity A_1, they will be noted G, P, A, the same applies for the other elements of G_1. For the other rollers, the elements G_i, P_i, A_i, etc. will be noted Gi, Pi, Ai on the figures.

(15) FIG. 1: the system is in the initial position Pos_0, in which a horizontal axis Ox, is an axis of symmetry of the assembly. The piston F is positioned so that the cavity A_1 is on this axis Ox, the 1.sup.st face G_1_1 is in its cavity.

(16) On this figure, we distinguish: O, the intersection of the cutting plane with the delta axis, P, and P2 the intersection of the cutting plane with the axes beta_1 and beta_2. They are the centers of cavities A and A2, and the rotation centers of rollers G and G2. The shape F, The envelope V, its end Qa toward the cavity A1 (in the position Pos_0), and the other end Qb.

(17) In this position Pos_0, V and G are in contact in Q.

(18) This point Q in the fixed reference frame Ox, Ow, is Q0 (0 for Pos_0).

(19) Qa is a point of V, which we will call Qa0,

(20) and a point of G, which we will call qa0. The rollers G, with a half-center angle μ the ends of which are R and S, with the axis of symmetry Py, and the roller G2, the ends of which are R2, and S2,

(21) On the other figures: ω is the angle of rotation (Ox, Oy) of the piston V, θ is the angle of rotation (Ox, Oz) of the roller G. Here, θ=2*ω (m=2).

(22) The initial data are: n equal to 2 m equal to 2 The distance d, equal to distance (OP) the radius r of the center angle (R,P,S) the half-angle μ of the center angle (R, P, S) of the roller G,

(23) From these data, we will draw the rest of the system.

(24) FIG. 2 corresponds to the position Pos_1, where the points Q, S and U meet.

(25) This figure allows determining w1, and the radius R of the shape F. Indeed, by observing the triangles, it is found that:
d*sin(ω1)=r*sin(μ+(m−1)*ω1), and
R=d*cos(ω1)+r*cos(μ+(m−1)*ω1)

(26) FIG. 3: it is question of determining the arc of curve G_1_2 of G.

(27) For this purpose, let's return in Pos_0. qa0 is a 1.sup.st point of G_1_2. Let's increase ω from 0 to ω1. At each time point t and at each value of ω(t), Qa is the point of V in contact with G in qa (qa being a point of G). The half-curve G_1_2 of G is the set of points qa.

(28) The last point is S. The other half-curve is obtained by symmetry.

(29) FIG. 4: the 1.sup.st portion of the envelope V is determined.

(30) For this purpose, let's start from Pos_1. Q is the 1.sup.st point of the researched envelope arc. Let's increase ω from ω1 until (P,S) becomes aligned with Ox. At each time point t and at each value of ω(t), S is the point of G in contact with V in s, s being a point of V.

(31) The 1.sup.st portion of the envelope V is the set of points s.

(32) FIG. 5, the position is Pos_2: (P,S) is aligned with Ox and ω=ω2. Let's increase ω from ω2 to 90°. This portion of the envelope V is an arc of circle with center O, with radius d-r.

(33) The rest of the piston is obtained, in this case, by 2 symmetries.

(34) We have hence seen that G_1_2 and the envelope V have been obtained independently. The curve G_1_2 has been <<machined>> by Qa (<<machine>> in the sense that Qa would be a cutting tool which would machine the material to give G_1_2 its shape, Qa and G_1_2 being driven in their respective rotational motions as precedingly defined), and the 1.sup.st portion of the envelope V has been <<machined>> by S.

(35) These curves have been obtained point-by-point to contribute to the understanding. They may also be obtained analytically.

(36) That was one approach. There are others. For example, assuming that we are led to consider that the ends Q of the piston must be larger, for example, for reasons related to sealing, manufacturing, or because the significant pressure at the moment of explosion, leads to enlarge the ends Q of the piston.

(37) The <<improved piston>> is then drawn, then it is this piston which will machine>> the rollers. This <<improved piston>> may be non-symmetrical; in this case, the curve arc G_I_2 is no longer symmetrical.

(38) For example, the shape of the piston Q may be rounded at its ends Qa and Qb, in order to be easier to machine (a rounded milling cutter is less expensive than the tools for machining more complex shapes). The principle remains the same, it is Qa which <<will machine>> the 1.sup.st portion of the arc G_1_2.

(39) Another example, if the ends of Q are no longer a tip, but 2 points Qaa, and Qab (for Qa) separated by a small distance compatible with the material strength constraints, and such that OQaa=OQab=d, to simplify, let's not take into account the shape of the piston between these 2 points, it is Qaa which <<will machine>> the 1.sup.st portion of the arc G_1_2 (the 2.sup.nd by Qab, which will be symmetrical).

(40) In a more general way, any modification relative to the basic drawing is possible, provided that the rollers G and the envelope V remain in contact at every time point, that is to say that one is the envelope of the other in their respective motions.

(41) FIGS. 6 to 11 show the operation of an engine with four rollers according to the invention.

(42) FIG. 6: the volume v2 has just been closed by the roller G2. It contains the fresh air to be compressed. In this example, the center angle μ=90°−ω1, so that the roller G2 closes v2, at the same time as the roller G4 opens the volume v1.

(43) FIG. 7: ω=ω1, the air volume v2 has been compressed and occupies the volume v3.

(44) FIG. 8: the volume v3 has passed in v4, on the other side of Qa by an adequate passage (not represented). At this time point the injection then the explosion may take place. The burnt gases exert a strong pressure on the central piston which makes it rotate.

(45) FIG. 9: It is the end of the expansion, the volume v4 has increased until becoming the maximum volume v5.

(46) FIG. 10: A quarter-turn is disposed to evacuate the burnt gases and fill the volume v6 with fresh air. The intake and exhaust valves are not represented.

(47) FIG. 11: the volume v7 contains fresh air, and the roller L1 closes the volume. We end up in the situation of FIG. 10.

(48) The exhaust and the intake may be performed in different ways and in accordance with the configuration. For example, here the exhaust may be performed at the level of f2 (FIG. 9). The intake may be performed at the level of e1 the bottom of the cavity v8 may be filled in advance with fresh air at low pressure, so that it will more quickly get rid of the remainder of burnt gases toward f2, upon the opening at the level of S.

(49) It may be found that, contrary to conventional cylinder engines, the valves (or clappers) are not in a fire area (where the explosion takes place) thus giving more freedom for their implementation.

(50) This operation resembles that of a two-stroke engine (compression, expansion, and exhaust/intake). We might describe an operation resembling that of a four-stroke engine, the complete cycle is then performed over 2 revolutions.

(51) FIGS. 12 to 16 show the influence of the center angle on the characteristics of the engine. These figures show, for different values of p, the maximum volume v5 for the expanded gases. The length d and the radius r are the same in all these figures.

(52) FIG. 12: μ=90°

(53) FIG. 13: μ=80: we see that, compared to the preceding case, for a difference of only 10°, the volume v5 is substantially larger, almost the double.

(54) FIG. 14: μ=66: we see that, compared to the preceding case, the volume has almost doubled again.

(55) FIG. 15: μ=90°-ω1 namely almost 60° here. For this value, the roller G_1 closes the preceding volume v8, and opens the volume v5 at the same time point. The volume v5 is slightly different relative to the preceding case: a ceiling is put.

(56) FIG. 16: μ=55°: we see that, compared to the preceding case, the volume v5 has slightly changed. It is found that for p<90°−ω1, the volume at the bottom of the cavity is never enclosed.

(57) We hence see that the maximum volume v5 has increased when μ has decreased, until to reach a ceiling and that the value to be retained is located in that vicinity, while taking into account different constraints.

(58) FIG. 17 shows that ω1 also passes through a maximum, obtained for about 65°. We also see that the distance OQ increases when μ decreases. Although this is not formally demonstrated here, the maximum of ω1 and the maximum of v5 are located in the same vicinity of values.

(59) These results have been explained for a particular value of the ratio r/d, but it might be demonstrated that they are general.

(60) What is true for the expansion of gases is also true for the compression because there is symmetry.

(61) This leads to the conclusion that μ=90° is not an ideal choice. For the engine to be more efficient, μ must preferably be lower than 90°.

(62) FIGS. 18A and 18B give an example of valveless operation, the fresh air passing by the inside of the central piston, and passing through the arc of circle shaped portion of this piston. The 2 intake valves fa and fb are represented. Only the exhaust valve f1 on G has been represented; there is one for each roller.

(63) The upwardly hatched area (by proceeding from left to right) corresponds to fresh air to be compressed, the downwardly hatched area corresponds to expanding burnt gases, the squared area corresponds to burnt gases, being replaced by fresh air.

(64) In the preceding figures, the rotation speed ratio is m=2.

(65) This rotation speed ratio m may be different. FIGS. 19 to 22 show some examples with coefficients m ranging from 3 to 5.

(66) FIG. 19: m=3 and 9 cavities.

(67) FIG. 20: m=4 and 9 cavities.

(68) FIG. 21: m=5 and 9 cavities.

(69) FIG. 22: m=5 and 11 cavities.

(70) FIGS. 23A and 23B show an example of driving with gears. The wheels G1 to G5 give the rotation direction and the ratio m.

(71) On FIG. 23B, the section AA, the sections of V and the rollers comprise (hatched) rectangles because all the generatrices are parallel to delta. But the rollers may be different, in particular at the outer angles. The envelope V is consequently modified. FIG. 23B shows chamfered rollers. They might also be rounded. More generally, any modification relative to the basic drawing is possible, provided that the rollers G and the envelope V remain in contact at every time point, that is to say that one is the envelope of the other in their respective motions.

(72) FIGS. 24 to 31A cover embodiments according to the 2.sup.nd implementation, that is to say, the shape F is in the inside, the envelope V is in the outside. Here, the shape F rotates, and the envelope V is fixed. The shape F is the central rotary piston.

(73) All what has been said for the 1.sup.st implementation and which remains valid for the 2.sup.nd is not repeated here.

(74) FIG. 24 shows the engine in the position Pos_0.

(75) FIG. 25 shows how to obtain ω1 and OQ.

(76) FIGS. 26 to 29 show the operation.

(77) FIG. 30 corresponds to FIG. 7 of the 1.sup.st implementation, with close rollers. The volume v3 of compressed air passes to the other side of the envelope V in v4 by a passage which is not represented.

(78) FIGS. 31A and 31B show an example of driving with gears.

(79) The rotary piston engine is presented as an intermediary solution between the engine with cylinders and pistons, and the turbine engine. The possible applications are numerous (engines, pumps, compressors, . . . ).

(80) Compared to the engines with cylinders and pistons, the removal of this considerably anti-mechanical reciprocating linear motion of the piston, the simplicity, the absence of vibration, will allow economical and reliable operations with little wear.

(81) Compared to the turbines (gas turbines, steam turbines, pressurized-fluid turbines, etc.), the efficiency will be considerably higher.

(82) This engine is also suitable for the carrying out of non-polluting gas engines or hydrogen engines.