EP0127694B1 - Engine with oscillating pistons and chambers - Google Patents

Description

The present invention relates to a piston machine with non-linear movements which can be used, inter alia, as an internal combustion engine, as a compressor, as a pump, etc. suppressing rectilinear movements of movable organs.

The object of the present invention is to provide a simple and robust construction machine, in which the problems of tightness, wear and maintenance are easy to master.

Such machines have been proposed, for example that described in patents CH-A-597,502 or US ― A ― 2,094,143. The machines according to the first sus-dil document have certain drawbacks, notably due to the fact that the pistons are driven in a rotational movement on themselves, which makes their kinematic connection with the machine shaft complicated and moreover entails sealing problems between the pistons along their articulation line and requires the use of pistons and spherical chambers. Without a continuous longitudinal shaft, these machines present torque transmission problems.

The pistons being driven in a rotational movement relative to the chambers in which they move only the spherical shape is usable. These relative movements which are not carried out only in one direction cause sealing difficulties between the pistons and their chambers.

In the machine described in US-A-2,094,143, the relative movement of the pistons, driven by a fixed central pivot on the motor shaft, is obtained using fixed cams.

Another problem of all internal combustion engines lies in the very high pressures existing between the pistons and their chambers which leads to significant deformations of these, even for example the ovalization of the cylinders and the wear of the pistons in the ordinary engines.

The present invention therefore also aims to achieve such a machine in which the pistons do not rotate on themselves during the operating cycle and have a simple angular movement relative to their chambers and in which the pressures between pistons and chambers, due to compressions and explosions, are eliminated.

The oscillating chamber and piston machine according to the present invention is distinguished by the characteristics listed in claim 1.

The appended drawing illustrates schematically and by way of example an embodiment and some variants of the machine according to the invention.

Figure 1 is a longitudinal couple, the pistons being in one of their extreme positions, the machine comprising a single active unit corresponding to a machine with two cylinders.

• La figure 3 est une vue partielle d'une variante, dans laquelle les chambres sont rectangulaires, en coupe suivant un plan perpendiculaire à l'arbre traversant et passant par l'axe du pivot central.
• La figure 4 est une vue partielle, schématique, de certaines parties mobiles de la machine dans la position illustrée à la figure 1.
• La figure 5 est une vue partielle, schématique correspondant aux organes illustrés à la figure 4, les pistons étant cette fois dans leur position médiane, la vue étant prise non pas de dessus, mais de côté.
• La figure 6 est une vue partielle de côté, certaines parties étant coupées, de la machine illustrée à la figure 1.
• Les figures 7 et 8 illustrent schématiquement le stator de distribution vu de A respectivement B (figure 1).
• La figure 9 illustre la face de distribution du stator de distribution d'une machine fonctionnant comme pompe ou compresseur avec un cycle à trois alternances de deux temps.
• La figure 10 illustre en coupe une seconde forme d'exécution de la machine.
• La figure 11 illustre très schématiquement une troisième forme d'exécution d'une machine comportant plusieurs unités actives reliées à un arbre moteur central.

FIG. 2 is a partial view from above, certain parts being cut off or cut away from the machine in its position illustrated in FIG. 1.

• Figure 3 is a partial view of a variant, in which the chambers are rectangular, in section along a plane perpendicular to the through shaft and passing through the axis of the central pivot.
• FIG. 4 is a partial schematic view of certain mobile parts of the machine in the position illustrated in FIG. 1.
• Figure 5 is a partial, schematic view corresponding to the members illustrated in Figure 4, the pistons being this time in their middle position, the view being taken not from above, but from the side.
• FIG. 6 is a partial side view, some parts being cut away, of the machine illustrated in FIG. 1.
• Figures 7 and 8 schematically illustrate the distribution stator seen from A and B respectively (Figure 1).
• FIG. 9 illustrates the distribution face of the distribution stator of a machine operating as a pump or compressor with a three-cycle two-cycle cycle.
• Figure 10 illustrates in section a second embodiment of the machine.
• FIG. 11 very schematically illustrates a third embodiment of a machine comprising several active units connected to a central drive shaft.

The machine illustrated in FIGS. 1 to 6 comprises a single active unit for the simplicity of the illustration and of its description. It is obvious that in practice, a machine could comprise several active units, four, six or more for example, coupled together.

This machine comprises a through shaft 1 journalled on a frame 2 in two bearings 3. A cylindrical central bearing 4 is carried by the shaft 1, the axis xx of this central bearing 4 is perpendicular to the axis of the shaft 1 This bearing 4 is made integral with the shaft 1 angularly using a key 5 and axially using a screw 6.

This cylindrical central bearing 4 serves as an articulation to a central pivot 7 whose longitudinal axis intersects the axis of the through shaft 1 at 0. This central pivot 7 is therefore angularly and axially integral with the through shaft 1, but can effect relative to the latter, oscillations in a plane defined by the axis of said central pivot 7 and that of the through shaft 1. The axis of the central pivot 7 can thus tilt relative to the axis of the traversing tree 1.

In this embodiment, the through shaft 1 simultaneously constitutes a motor member of the central pivot 7 to which it is mechanically connected.

The illustrated unit machine further comprises two chambers 8, 9 each formed by a first external shell 10 and a second internal shell 11, the upper and lower ends of which are adjusted to one another and connected together as well as to the ends of the pivot. central 7 using locks 12 rendered secured to the central pivot by screws 13.

Each outer shell 10 has a cylindrical boss 14 whose axis passes through the intersection 0 of the axes of the central pivot 7 and of the through shaft 1 and is perpendicular to these two axes.

A circular distribution ring 15 surrounds the two outer shells 10 and has two recesses receiving the bosses 14 of these shells 10. This distribution ring 15 is thus angularly integral with the shells 10 and therefore with the central pivot 7 and the through shaft 1 .

Seals are provided between the shells 10 and the distribution ring.

A passage 16 is made in the cylindrical bosses 14 of the external shells 10 connecting the chamber 8 respectively 9 to a precombustion recess 17, respectively 18 practiced in the distribution ring 15. These recesses 17,18 communicate, as will be seen more away, by a passage 19.20 with lights 21 made in the frame 2, these lights being themselves connected to the suction or discharge pipes respectively of the machine, as well as to the ignition device of the machine.

Seals are provided between the distribution ring 15 and the frame 2.

The unitary machine illustrated also comprises two double pistons 22,23, each having two active faces 24,24a, 25,25a respectively evolving freely in chambers 8 and 9. These active faces 24,25 of the pistons consist of added parts 26 on the pistons 22,23. These inserts 26 can slide in their plane relative to the pistons so as to ensure self-centering of the latter in the chambers 8, 9. These inserts 26 comprise sealing elements, for example in the form of segments, ensuring a perfect seal between their edges and the internal walls of the chambers 8, 9 formed by the shells 10, 11.

The pistons 22, 23 each have a recess 27 giving passage to the through shaft 1 and comprise arms 28 at their upper and lower ends respectively. These arms 28 carry guide shoes 29 sliding in a bowl 30 formed in the ends of the central pivot 7. In this way the pistons are held in a fixed axial position relative to the central pivot 7 and are pivoted concentrically to this pivot, on this one.

These arms extend beyond the upper and lower ends of the active faces of the pistons.

In this way, it ensures perfect guidance of the pistons in the chambers and they move freely in the chambers without contact with them other than those due to the sealing segments.

The illustrated unit machine also includes eccentrics 31, 32 journalled in the example illustrated concentrically with the through shaft 1 and the active parts 33, 34 of which have axes joining at the point 0 of intersection of the axes of the central pivot 7 and of the through shaft 1. These active parts of the eccentrics rotate in housings 35,36 formed in the pistons 22,23. It should be noted that each of the active parts of the eccentrics 33, 34 is traversed right through by the traversing shaft 1, which allows a construction in which these eccentrics are large, dimension while ensuring a large angle between the axes of these eccentrics and the axis of the through shaft 1, allowing a large angular displacement of the pistons relative to each other.

This unitary machine also comprises kinematic means imposing a relative rotation between at least one of the eccentrics 31,32 and the through shaft 1. In the example illustrated, the two eccentrics 31,32 are driven in rotation relative to the shaft crossing 1. A first kinematic link connects the eccentric 31 to the through shaft 1 and a second kinematic link connects the eccentric 32 also to this through shaft 1.

The kinematic connection between the eccentric 31 and the through shaft 1 comprises a toothed pinion 37 integral with the eccentric 31 and concentric with the through shaft 1, meshing with a satellite pinion 38 pivoted idly on an axis 39 integral with a connecting rod 40 itself secured to the through shaft 1 using a key 48 and a screw 49. This idler satellite pinion 38 also meshes with a toothed ring 41 rigidly fixed on the frame 2. The ratio of reduction of this kinematic connection is such that the eccentric 31 rotates around the through shaft 1 at a speed V2 always greater than the speed of rotation V1 of the through shaft 1 and in the same direction as the latter.

The kinematic link connecting the eccentric 32 to the through shaft 1 comprises a pinion 42 secured to the eccentric and concentric to the through shaft 1 meshing with a first satellite pinion 43 pivoted idly on an axis 44 secured to a connecting rod 45 itself secured to the through shaft 1 using a key and a screw. This connecting rod 45 carries a second axis 46 on which is journalled a second satellite pinion 43a engaged, on the one hand, with the first satellite 43, and on the other hand, with a toothed crown 47 secured to the frame 2. The ratio of reduction of this kinematic connection is such that the speed of rotation V3 of the eccentric 32 around the traversing shaft 1 is identical in absolute value to the speed of rotation of the eccentric 31 around this same shaft, but in direction opposite. We thus ensure by these kinematic links the relation N21 = N3 /> V1. In this example of a machine, each piston 22, 23, executes inside the corresponding chamber 8, 9, two alternations for a revolution of the through shaft 1. To obtain these four movements of each piston, the gear ratio kinematic links is 1: 2. By modifying these ratios, a different number of piston alternations is obtained per revolution of the through shaft.

In FIG. 3, we can see the detail of the attachment of the shells 10, 11 to the central pivot 7 using the latches 12 and the screws 13.

We see that the upper edge of the outer shell 10 is placed on a shoulder formed in the upper edge of the inner shell 11. The latches 12 come to cap these two shells 10,11 to keep them in an axial position relative to the pivot 7 and simultaneously thanks to the external shoulder of the lock, the latter also blocks the radial position of the shells 10, 11 relative to the central pivot 7. This fixing also makes it possible to ensure sealing between the edges in contact with the shells.

This FIG. 3 shows a variant in which the chambers 8, 9 have a rectangular section. This is without other possible, owing to the fact that compared to these chambers 8,9 the pistons 22,23 carry out a simple angular movement constituted only by a rotation around the central pivot 7 whose chambers are integral and concentric.

• 1. Lords de la rotation de l'arbre traversant 1, la rotation de l'anneau de distribution 15 s'effectue à la même vitesse V1 et ceci sans aucune translation ou inclinaison de cet anneau 15. Ceci facilite grandement l'alimentation et l'échappement des chambres 8,9.
• 2. Du fait de la rotation relative des excentriques 31,32 entre-eux et par rapport à l'arbre traversant 1, les faces actives des pistons 22,23 se rapprochent respectivement s'éloignent provoquant une modification du volume des chambres 8,9.

The very particular construction and design of the machine described requires that a certain number of characteristics which are derived from it are particularly noted:

• 1. Lords of rotation of the through shaft 1, the rotation of the distribution ring 15 takes place at the same speed V1 and this without any translation or inclination of this ring 15. This greatly facilitates feeding and l exhaust from chambers 8.9.
• 2. Due to the relative rotation of the eccentrics 31,32 between them and relative to the through shaft 1, the active faces of the pistons 22,23 approach each other move away respectively causing a modification of the volume of the chambers 8,9 .

During this movement, the axis of the pistons describes a cone, the apex of which coincides with the point 0 of intersection of the axes of the central pivot 7 and of the through shaft 1, without the pistons turning on them- same, because of the sliding between these and their eccentrics. This is made possible by the fact that the pistons have a large opening giving passage to the through shaft 1. This opening is at least equal in surface to the intersection of the piston with a conical surface whose apex is located at point 0 and whose the base consists of the edges of the active part of the corresponding eccentric.

Still during this movement, the central pivot 7 performs an angular oscillation, causing in it the chambers 8,9 and the shells 10,11 which are integrally connected to it, around the cylindrical central bearing 4, causing a modification of the inclination the axis of this central pivot 7 relative to the axis of the central shaft 1.

A rotational movement takes place between the active parts of the eccentrics 33,34 and the respective pistons 22,23, so that these pistons do not rotate on themselves, although the eccentrics 31,32 do rotate around them of the axis of the through shaft 1.

This has the consequence that the movement of the pistons 22,23 with respect to the chambers 8,9 is a simple pivoting around the central pivot 7. Therefore, the chambers do not necessarily have to be spherical, but can have any shape provided that the external and internal surfaces of these chambers are surfaces of revolution having as their axis the axis of the central pivot 7. It is thus possible to design chambers whose external or internal generator is curvilinear, in a circular arc, broken, rectangular, etc.

3. As seen in Figure 4, when the eccentrics are in opposition, the central pivot 7 is perpendicular to the through shaft 1. In this position, the pistons 22,23 are in one of their extreme positions. On the other hand, when the eccentrics are located in parallel planes, their axes then being combined, the central pivot 7 has a maximum inclination relative to the axis of the through shaft 1. In this position, the pistons are in their position median (Figure 5).

4. The active parts of the eccentrics 33,34 can be very large without limiting the opening angle between two active faces of the two pistons 22,23 thanks to the fact that these eccentrics are placed very close to the center of the unit and that they can move inside the rooms 8,9. This arrangement is possible, due to the large opening of the pistons allowing them to move around the transverse axis 1.

5. The distribution ring 15 rotates at the same speed and in the same direction as the through shaft 1, these elements can be rigidly connected to each other, for example by a casing. This casing would replace the connecting rods 40,45 and would carry the satellites 38,43 and 43a. This makes it possible to stiffen the entire construction and not to transmit all the torque through the shaft 1, but to take over part of it through this distribution ring 15 and the casing. It is thus possible to produce a very compact motor comprising an external distribution ring, but of small diameter all the same which is important for high rotational speeds.

6. The forces are equally distributed over the two large eccentrics.

7. The pistons exert no force against the walls of the chambers, just like those due to the sealing rings. This greatly limits wear on the pistons and chambers. The active surfaces of the pistons are self-centered.

8. Several units can be mounted in rows on the same traversing tree. In this case, the units are mounted so that the central pivots oscillate in opposition to balance the whole.

9. It is known that during the explosion or combustion of a gas mixture, the gases tend to be violently projected towards the outside. This is favorable in this construction since the pistons have a larger active surface outward than in the center. The strength of the exploit sion is distributed on two active faces and therefore on two bearings of the eccentrics better distributing the forces for example in the case of a diesel engine.

10. The machine is well balanced owing to the fact that the two chambers are integral with the central pivot and that the imbalances formed by the pistons and the eccentrics can be easily compensated by balancing weights.

• a).assurer un rapport de démultiplication entre l'arbre traversant 1 et les excentriques 31 respectivement 32 de 1:1 2 respectivement de 1:-2. Ainsi, pour une révolution complète de l'arbre traversant 1 les pistons effectuent deux aller et retour dans leur chambre respectivement, ce qui correspond à un cycle complet.
• b) prévoir que les chambrages 17, respectivement 18 de l'anneau de distribution 15 afférant aux chambres 8, respectivement 9 débouchent sur deux côtés opposés de cet anneau de distribution 15.
• c) prévoir des lumières dans le côté droit du bâti 2 (figure 8). Une lumière d'admission 50 d'approximativement 90° suivie d'une zone fermée d'approximativement 90°. Un point d'allumage 51 à cet endroit constitué par exemple par une bougie, suivi d'une nouvelle zone fermée d'environ 90° qui elle est suivie par une lumière d'échappement 52 s'étendant sur approximativement 90°.
• d) prévoir dans le côté gauche du bâti 2 (figure 7) les mêmes lumières 50,52 et un point d'allumage 51, mais décalées de 90° par rapport au côté droit du stator.

To operate the machine as a four-stroke internal combustion engine (Figures 7 and 8) you can:

• a). ensure a reduction ratio between the through shaft 1 and the eccentrics 31 respectively 32 of 1: 1 2 respectively of 1: -2. Thus, for a complete revolution of the shaft passing through 1, the pistons go back and forth in their chamber respectively, which corresponds to a complete cycle.
• b) providing that the recesses 17, respectively 18 of the distribution ring 15 relating to the chambers 8, respectively 9, open on two opposite sides of this distribution ring 15.
• c) provide lights in the right side of frame 2 (figure 8). An inlet light 50 of approximately 90 ° followed by a closed area of approximately 90 °. An ignition point 51 at this location constituted for example by a spark plug, followed by a new closed zone of approximately 90 ° which is followed by an exhaust light 52 extending over approximately 90 °.
• d) provide in the left side of the frame 2 (FIG. 7) the same lights 50, 52 and an ignition point 51, but offset by 90 ° relative to the right side of the stator.

This staggered arrangement of lights and ignition points is necessary because when a room has its minimum volume, ie at the start of admission, the other room is at its maximum volume. However, as the ignition point is 180 ° from the start of the intake, it can be seen that a shift of the intake, exhaust and ignition devices of 90 ° is necessary between the two chambers 8 and 9.

To operate the machine as a compressor (Figure 9), you can for example:

a) ensure a ratio of 1: 3 respectively 1: -3 between the eccentrics 31, respectively 32 and the through shaft 1.

Thus, for each complete revolution of the shaft 1 the pistons of the same chamber perform three alternations.

b) as the cycle has only two phases, compression and admission, it is possible to open the recesses 17,18 on the same side of the distribution ring and provide a succession of lights on the stator, with a span of 60 ° approximately, alternately intake 53 and exhaust 54.

Many variants of this machine are conceivable. We could provide a single chamber and two single pistons and not double. Similarly, one can provide a single single or double piston cooperating with one, respectively two chambers. In this case, the chambers are closed at one of their front ends by a fixed member.

Provision could also be made for the traversing shaft to be fixed and for the kinematic connection means to drive the eccentrics 31 and 32 in rotation around the traversing shaft 1 at equal speed and in the opposite direction.

Under such conditions, the pistons only carry out a pivoting movement around the axis of the central pivot 7 and an oscillation corresponding to that of this central pivot. The chambers 8, 9 only oscillate on themselves around the bosses 14. For the distribution of such a machine with a fixed through shaft, it is possible to provide valves, or any other system of lights between the oscillating parts and the fixed frame.

It is also possible to provide chambers of different dimensions, the pistons then each having a large and a small active surface. Such a construction makes it possible to produce two-stage compressors.

A second embodiment of the machine is illustrated in FIG. 10. This machine also includes a single active unit to simplify the description and its representation. This machine comprises a fixed frame 70 containing all the moving parts of the machine. This machine also comprises two pistons 71, 72, each having two active faces 73, 74; 73a, 74a formed, as in the first embodiment described by attached parts which can move relative to the pistons parallel to the active faces 73, 74 to ensure self-centering of these in the chambers 75, 76.

These pistons 71, 72 are, as in the first embodiment, guided axially and radially on a central pivot 77. The external surface of this central pivot 77 constitutes the internal surface of the chambers 75, 76. The external surfaces of these chambers 75, 76 are here also produced by shells 78 integral with the central pivot and having pins 79 coaxial and perpendicular to the axis of the machine and to the axis of the central pivot 77 and passing through the point of intersection 0 of these two axes.

These pins 79 have passages 80 and are engaged in housings made in a distribution box 81 comprising passages 82 communicating on the one hand with the passages 80 and on the other hand with intake ports 82 a and exhaust , as well as an ignition member in the case of an internal combustion engine, practiced in, or fixed to the frame 70.

The machine further comprises two eccentrics 83, 84 whose active parts constituted by pins 85, 86 are housed in corresponding bearings made in pistons 71, 72. The eccentric 84 is journalled on a shaft 87 rigidly fixed to the frame 70 and extending coaxially to the longitudinal axis of the machine. This eccentric 84 has a coaxial pinion 88 to the fixed shaft 87 kinematically connected to a ring gear 89 by means of two satellites 90, 91 pivoted idly on axes integral with the distribution box 81.

The other eccentric 83 is journalled on a control member, formed here by a motor shaft 92, pivoted in the frame coaxially with the longitudinal axis of the machine.

This motor shaft 92 is rigidly fixed on the distribution box 81. The eccentric 83 carries a pinion 93 kinematically connected to a ring gear 94 secured to the frame 70 using a satellite 95 pivoted idly on an axis secured to the housing distribution 81.

It should also be specified that here also the axes of the active parts 85, 86 of the eccentrics both pass through the point 0 of intersection of the longitudinal axis of the machine and the axis of the central pivot 77.

The kinematic connections 93, 94, 95 connecting the eccentric 83 to the distribution box 81 and 88, 89, 90, 91 connecting the eccentric 84 to this same distribution box 81 have relationships such as with respect to this distribution box 81, the eccentrics rotate at the same relative speed, but in opposite directions.

In this embodiment, the machine does not have a through shaft and the central pivot is only held by the distribution box 81 by means of the shells 78 of which it is integral.

It should be noted that the removal of the through shaft is made possible by the fact that an active double piston unit as described does not cause any axial thrust in the direction of the longitudinal axis of the machine, since the chambers 75, 76 are integral with the central pivot 77. All the energy developed in the chambers 75, 76 is transmitted to the drive member or drive shaft 92, by the eccentrics, the kinematic connections and the distribution box.

It is obvious that we can provide variants of this second embodiment of the machine in which there could be a single double piston or a single chamber cooperating with one or two simple pistons.

The third embodiment of the machine illustrated in FIG. 11 is a machine comprising several active units, four in the example illustrated.

This machine comprises two groups of two units mounted in parallel on a drive shaft 100. Each of the groups comprises two units mounted in series on a through shaft 101.

In this embodiment, each active unit comprises a central oscillating pivot 102 rotatably mounted on a through shaft 101. This central pivot 102 is rigidly connected, as in the embodiments previously described, to two chambers constituted by shells 103 integral in rotation of the distribution box 104 around the through shaft 101. In this embodiment, a distribution box 104 cooperates with two active units. As in the embodiments previously described, this distribution box 104 cooperates with the fixed frame 105 and alternately connects the chambers of the active units to the intake 106 and exhaust 106a ports made in this frame 105. Channels 107 of the distribution box 104 and 107a shells 103 are provided for this purpose.

In this embodiment, each active unit also comprises two pistons 108, 109 whose active surfaces move inside the chambers 110, 111. These pistons are guided on the ends of the central pivots 102 as in the forms of previous execution.

Likewise, these pistons 108, 109 are mounted rotating on the active parts of eccentrics 112, 113, the axes of which intersect at the points of intersection of the axes of the central pivots 102 and of the through shaft 101.

The eccentric 112 of each active unit is here integral with the through shaft 101, while the other eccentric 113 of each active unit is journalled concentrically with the through shaft and is connected by a kinematic link to the distribution box 104, which constitutes in this execution the control member.

This kinematic link comprises a pinion 114 integral with the eccentric 113, coaxial with the through shaft 101, meshing with a satellite pinion 115 idly pivoted on an axis carried by the distribution box 104 and simultaneously engaged with a toothed crown 116 integral of the fixed frame 105. This kinematic connection is such that the eccentric 113 rotates around the through shaft 101 in the same direction as the distribution box 104, but at higher speed.

In this embodiment, the distribution box 104 constitutes the drive member of two coaxial active units.

One of the eccentrics 113 carries a pinion 117 coaxial with the through shaft 101 and meshing with a toothed wheel 118 secured to the motor shaft 100.

Finally, this drive shaft 100 further comprises a pinion 119 engaged with a satellite pinion 120 journalled idly on an axis integral with the fixed frame 105. This satellite 120 meshes with a toothed wheel 121 integral with the through shaft 101.

The ratios of the various kinematic connections described are always such that the relative rotational speeds of the eccentrics 112, 113 with respect to the control member, here the distribution box 104, are equal, but in opposite directions.

In the example illustrated, the ratio between the gear 118 and the gear 117 is 1.5: 1, that between the gear 119 and the gear 121 1: 2 and that between the eccentric 113 and the housing distribution 104, i.e. the kinematic link 114, 115, 116, of 1: 2.

Thus, when the distribution box 104 rotates in one direction, the eccentric 113 performs, relative to the housing 104, two rotations in the same direction and the eccentric 112, integral with the through shaft 101, performs two rotations in the opposite direction. Thus, compared to the frame 105, a revolution of the distribution box tion 104 corresponds to three revolutions in the same direction of the eccentrics 113 and to one revolution in the opposite direction of the eccentrics 112.

In this way, one turn of the motor shaft 100 corresponds to 1/2 turn of the distribution box 104, that is to say an opening and a closing of the pistons 108, 109.

The arrangement of this third embodiment of the machine is very compact, it allows the coupling of several groups of active units in a limited space, grouped around a single motor shaft.

• 1. Une ou plusieurs chambres solidaires d'un pivot central oscillant.
• 2. Un organe moteur solidaire des chambres en rotation autour d'un axe coaxial à l'axe de rotation du ou des excentriques.
• 3. Des liaisons cinématiques imposant des rotations relatives des excentriques, par rapport à un organe moteur, de même vitesse, mais de sens opposé. Ceci se retrouve toujours que l'organe moteur soit constitué par l'arbre traversant ou par le boîtier respectivement l'anneau de distribution.
• 4. Des pistons, montés tournant sur les parties actives des excentriques et guidés axialement et angulairement par rapport au pivot central oscillant, dont les surfaces actives se déplacent dans les chambres pour en faire varier le volume. Le mouvement des pistons dans les chambres est toujours uniquement un pivotement autour du pivot central dont les chambres sont solidaires.
• 5. De préférence, les pistons sont pivotés autour d'un pivot central oscillant pour éviter toute friction entre ceux-ci et les chambres autres que celles dues aux organes d'étanchéité.

In general, the following essential characteristics are always found in all possible embodiments of the machine according to the invention:

• 1. One or more chambers integral with an oscillating central pivot.
• 2. A motor member integral with the chambers in rotation about an axis coaxial with the axis of rotation of the eccentric or eccentrics.
• 3. Kinematic connections imposing relative rotations of the eccentrics, with respect to a drive member, at the same speed, but in the opposite direction. This is always found whether the drive member is constituted by the through shaft or by the housing respectively the distribution ring.
• 4. Pistons, mounted rotating on the active parts of the eccentrics and guided axially and angularly with respect to the oscillating central pivot, the active surfaces of which move in the chambers to vary their volume. The movement of the pistons in the chambers is always only a pivoting around the central pivot whose chambers are integral.
• 5. Preferably, the pistons are pivoted around an oscillating central pivot to avoid any friction between these and the chambers other than those due to the sealing members.

Claims (29)

1. Machine having oscillating chambers and pistons comprising at least one central pivot (7;77;102) driven in rotation by a motor member (1;92;104); and at least one piston (22;71;108) pivoted concentrically to the axis of the central pivot (7;77;102) comprising at least one active surface displacing itself within at least one chamber (9;76;111) in orderto modify its volume; the walls (10,11;78;77;103,102) of this chamber (9;76;111) being fast with the central pivot (7;77;102) and fast for rotation around the longitudinal axis of the machine with a distribution member (15;81;104); the inside wall (11 ;77;102) of said chamber (9;76;111) having the shape of a surface of revolution the axis of which coincides with the one of the central pivot (7;77;102); characterized by the fact that the piston (22;71;108) is rotatively mounted on an active part of an eccentric (33;83;113) the axis of the active part of which passes through the intersection (0) of the axes of the motor member (1;92;104) and of the central pivot (7;77;102); by the fact that it comprises kinematic linkage means (31,38,41;93,94,95;114,115,116) imposing a relative rotation between the eccentric (33;83;113) and the motor member (1;92;104); by the fact the outside wall (10;78;103) of this chamber (9;76;111) is formed of a shell journaled on the distribution member (15;81;104); and by the fact the central pivot (7;77;102) is mounted oscillating around a direction perpendicular to the axis of the motor member (1;92;104).

2. Machine as claimed in ctaim 1, characterized by the fact that the motor member (1) is formed by a passing axle; and by the fact that the piston (22) is provided with an opening (27) giving passage to the passing axle (1). (Figure 1).

3. Machine as claimed in claim 1, characterized by the fact that the motor member (92) is formed by a shaft, pivoted on to the frame (70), rigidly connected to a casing (81) which is angularly fast, around the axis of the motor shaft (92) with the chamber (76). (Figure 10).

4. Machine as claimed in claim 1, characterized by the fact that the motor member (104) is formed by a casing angularly fast, around its axis, with the chamber (111) this casing (104) being driven in rotation through a motor shaft (100), pivoted on the frame (105), through the intermediary of a kinematic linkage (118,117,116,115). (Figure 11).

5. Machine as claimed in claim 4, characterized by the fact that it comprises a passing axle (101), free angularly with respect to the central pivot (102) and passing through the piston (108); as well as a second eccentric (112) fast with the passing axle (101).

6. Machine as claimed in 2,3, or 4, characterized by the fact that during one revolution, the eccentric (33;83;113) penetrates inside of a chamber (9;76;111).

7. Machine as claimed in claim 6, characterized by the fact that the eccentric (33;83;113) penetrates inside of the area of the chamber (9;76;111) which is scanned by the active face of the piston (22;71;108).

8. Machine as claimed in claim 2 or claim 5, characterized by the fact that the active portion of the eccentric (33; 113) is passed through by the passing axle (1;101).

9. Machine according to one of the claims 1 to 8, characterized by the fact that it comprises a second chamber (8;75;110) fast with the central pivot (7;77;102), opposite the first chamber (9;76;111), inside which moves a second active face of the piston (22;71;108) causing a variation of the volume of said second chamber (8;75;110) in the opposite sense to the volume variation of said first chamber (9;76;111).

10. Machine as claimed in one of the preceding claims, characterized by the fact that it comprises a second piston (23;72;109) turning on a second eccentric (34;84;112) the axis of the active portion of which passes through the intersection (0) of the axis of the central pivot (7;77;102) and of the motor member (1,92,104) and kinematic linkage means (42,43,43a,47;89 to 91; 118,120,121) imposing to said second eccentric (34;84;112) a more rapid rotation than, and in the same direction as, the.control member (1;92;104).

11. Machine as claimed in one of claims 1 to 9, characterized by the fact that it comprises a second piston (23;72;109) turning on a second eccentric (34;84;112), the axis of which passes through the intersection of the axes of the central pivot (7;77;102) and of the motor member (1;92;104) and kinematic linkage means causing said second eccentric to rotate, with respect to said motor member (1;92;104), at the same speed as the first eccentric (3-3;83;113), but in opposite direction; and by the fact that this second piston (23;72;109) comprises one, respectively two active faces moving in the chamber or the chambers (8;75;110; 9;76;111).

12. Machine as claimed in claim in one of the preceding claims, characterized by the fact that each chamber (8;75;110; 9;76;111) constituted by a shell (10;78;103) forming the outside wall of the chamber, the internal wall of said chamber being constituted by the external surface of the central pivot (7;77;102).

13. Machine according to one of the claims 1 to 12, characterized by the fact that each chamber (8;75;110; 9;76;111) is constituted by a shell (10;78;103) forming the outside wall of the chamber, the internal wall of the chamber being made by a second shell (11) tightly connected with the first one.

14. Machine as claimed in claim in claim 12 or claim 13, characterized by the fact the shell or shells (10;78;103; 11) of each chamber (8;75;110; 9;76;111) are fast to the central pivot (7;77;102) by means of locks (12) mounted onto the central pivot (7;77;102).

15. Machine as claimed in one of claims 1 to 14, characterized by the fact that each piston (22,23;71,72;108,109) is guided axially and radially on the central pivot (7;77;102).

16. Machine as claimed in claim 15, characterized by the fact that the guiding members of the piston (22,23;71,72;108,109) are located beyond the upper and lower ends of the active faces of the pistons.

17. Machine as claimed in claim 16, characterized by the fact that the two pistons (22,23;71,72;108,109), as well as their guiding members, are identical and that each piston has two orthogonal symmetry axes.

18. Machine as claimed in claim 9 or in claim 10, characterized by the fact that the chambers (8,9;75,76;110,111) have different dimensions.

19. Machine as claimed in one of the preceding claims, characterized by the fact that each piston (22,23;71,72;108,109) comprises at least one active surface formed by a built-up part carrying sealing elements, and by the fact that this built-up part is fixed onto the piston, with clearance in its plane, permitting a self centering.

20. Machine as claimed in one of the preceding claims, characterized by the fact that the internal faces of the outside shells (10;78;108) of the chambers (8,9;75,76;110,111) are portions of spheres.

21. Machine as claimed in claims 2 and 11, characterized by the fact that the kinematic linkage means connect each eccentric (33;34;113) to the passing axle (1;101).

22. Machine as claimed in claims 3 and 11, characterized by the fact that the kinematic linkage means connect the two eccentrics (83,84) to the control casing (81).

23. Machine as claimed in claim 4 and 11, characterized by the fact that one kinematic linkage means connects one of the eccentrics (113) to the control casing (104), the second eccentrics (112) being fast with the passing shaft (101), and a second kinematic linkage means connects the eccentric (113) to the motor shaft (100) and a third kinematic linkage means connects the motor shaft (100) to the pasing shaft (101).

24. Machine as claimed in claims 1 and 11, characterized by the fact that the relative rotation between the eccentrics (32,33;83,84;112,113) and the central pivot (7;77;102) have the same speed but opposite directions.

25. Machine as claimed in claims 4 and 11, characterized by the fact that the kinematic linkage means connecting each eccentric (112,113) to the motor member (104) include an outside shaft (100).

26. Machine as claimed in claim 2 or claim 11, characterized by the fact that it comprises a distribution ring (15) angularly fast around the passing shaft (1) with the chamber or chambers (8,9) around the longitudinal axis of the machine.

27. Machine as claimed in claim 26, characterized by the fact that the distribution ring (15) comprises a precombustion chamber (17,18) associated to each chamber (8,9) and permanently connected therewith through a channel (16).

28. Machine as claimed in claim 4, characterized by the fact that it comprises one casing (104) for several active units.

29. Machine as claimed in claim 28, characterized by the fact that this casing (104) comprises at least one bearing located between the active units in which one of the eccentrics (112) of each unit is journaled.

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