MXPA00008344A - Rotary-piston machine - Google Patents

Abstract

A rotary-piston machine (10) comprising a housing (5) having a cavity (9), a rotor (2) received in the housing (5), which rotor (2) having a rotor axis (A) and a peripheral surface (21), inlet and outlet passages (3, 4) in communication with said cavity (9), one or more vanes (1) radially slideable received in slots (11) in the rotor (2), each vane (1) extending radially from the internal surface (20) of the housing (5) to the rotor axis (A), and at least one working chamber (9a) being part of the cavity (9) and is defined by the internal surface (20) of the housing (5), the peripheral surface (21) of the rotor (2) and the side surface of at least one vane (1). Each vane (1) is articulated connected about an axis (C) to one end of a control arm (7) and is in the other end pivotable journalled in a fixed axle shaft (8) having a central axis (B) being coincident with the axis extending centrally through the cavity (9) of the housing (5), which axis (B) extend in parallel with and spaced (d) from the rotor axis (A), and the rotor (2) proper constitute the unit for power take off or power input.

Description

ROTATING PENKNIFE MACHINE FIELD OF THE INVENTION The present invention relates to a rotary piston machine comprising a box having a cavity, a rotor received in the box, the rotor having a rotor shaft and a peripheral surface, input passages and output in communication with the cavity 1 or more radially slidable vanes received in recesses in the rotor, each vane extends radially from the inner surface of the box to the rotor shaft, and at least one working chamber is part of the cavity and is defined by the internal surface of the box, the peripheral surface of the rotor and the lateral surface of at least one blade. The rotary piston machine is a thermo-dynamic machine, which with some modifications can be used as a combustion machine, heat exchanger, pump, vacuum pump and compressor. The rotary machine can be assembled in several units and in series, so that the principle of the machine is used for both the compressor unit and the combustion machine unit in a supercharged machine. It must be specified previously that the rotating machine does not have a crankshaft and the power supplied or taken from the machine is made directly from or from the rotor.

BACKGROUND OF THE INVENTION The prior art combustion machines of the rotary type are embodied as rotary piston machines, here the rotary piston rotates plunger which is in the form of a rotor having a triangular design arched in an annular cylindrical bore. Such combustion machines also have a complicated design, the disadvantage that the rotor presents considerable problems of sealing against the cylinder wall. In addition, these combustion engines have a large fuel consumption. A prior art combustion engine comprises a machine box having a work machine that receives a rotating rotor continuously, and an inlet and outlet for the combustion gases, which is known from DE-3011399; the rotor is basically cylindrical and rotates in an elliptically designed cavity comprising opposing combustion chambers diametrically defined by the surface of the rotor and the internal surface of the cavity. The rotor is designed with radially extending sliding recesses, which receive and guide vane pistons which are capable of sliding radially outwardly and inwardly in the sliding recesses. The vanes are articulated in connection with a connecting bar with a crankpin that is also part of a journal crankshaft. When the rotor is rotating, the plunger blades move radially outward and inward in the sliding recesses, due to a fixed support on the crankpin. Thus, a set of blades acts in one part of the cavity, that is, in a combustion chamber while the other set of blades acts in the diametrically opposite chamber. U.S. Patent 4,451,219; presents a rotary steam machine that has two chambers and no valves, also the machine has two sets of blades or rotating blades with three blades in each set. Each set of rotor blades rotates around its own eccentric point on a common stationary crankshaft inside an elliptical machine case. A rotor of the drum type is mounted centrally in the machine housing and defines two radially opposed working chambers diametrically. The two sets of rotor blades move basically radially outwards and inwards in sliding recesses in the rotor according to the machine described above. The vanes are also here at their central end supported on an eccentrically located shaft or rod which is fixed. However, the vanes are not articulated but are on the end pivot table mounted on a bearing provided peripherally on the rotor. Bombs and compressors of the type of alabe are also known. The patent US 4,451,218; refers to a blade pump having rigid blades and a rotor that is eccentrically supported in the pump housing. The rotor has recesses through which the blades pass radially and are guided by them. Seals or sealings are provided on each side of the sliding recesses. The patent US 4,385,873; shows a rotary machine of the type of blade that can be used as an engine, compressor or pump, it also has a rotor mounted eccentrically passing a number of rigid blades through it radially. Other examples of the prior art are presented in US 4,767,295 and US 5,135,372. SUMMARY OF THE INVENTION An object of the present invention is to provide a rotary piston machine having high efficiency, low fuel consumption and low emissions of polluting substances such as carbon monoxide, nitrous gases and unburned hydrocarbons. Another object of the present invention is to provide a rotary piston machine of a compact design, that is, a small displacement volume of the machine and a small overall volume with respect to the power produced. According to the present invention, a rotary piston machine of the type described in the introductory part of the specification is provided, and it is distinguished because each blade is hingedly connected about one axis to one end of a control arm and the other The end is pivotally mounted in a pivot in a fixed shaft having a central axis coinciding with the axis extending centrally through the cavity of the box, the shaft extending parallel to and spaced from the rotating shaft, and the rotor properly speaking it constitutes the unit to receive power or to give it. The above-described embodiment is a clean rotary piston machine that can be a compressor or combustion machine with or without an external compressor. Preferably, each blade tip describes a cylindrical surface sector having a center of curvature on the shaft through the joint connecting the blade to the control arm. The idea of this is that the blade tip along a line extending parallel to the rotor axis at all times is tangent to the inner surface of the cavity, even if it does not touch the surface. This line will move on the tip of the blade during rotor rotation, and at all times will describe a cylindrical surface that is approximately similar to the inner surface of the case, with a difference only in the tolerance present between the tip of the blade and the blade. internal surface of the box. The tolerance between the tip of the blade and the internal surface of the cavity should be as small as possible. It should be noted that the thickness of the blade can be greater without obtaining or taking any effect for sealing against the internal surface of the cavity. However, if the thickness of the blade is less than optimal, a tangent of the blade tip against the inner surface of the cavity will not be obtained in the parts of the blade revolution with the rotor, and will normally be needed. a sealing of the tip of the blade. The thinner the blade is with respect to what is optimal, the greater the area of the blade tip that will not be tangent to the inner surface of the cavity. In some embodiments, it may be appropriate to provide sealing means between the tip of the blade and the inner surface of the box. Preferably, in the sealing or sealing means it is provided on the tip face of the blade and the sealing means sweeps against the internal surface of the cavity. In some conditions, it may be suitable to provide sealing means between the blade recesses in the rotor and at least one side face of the blade. In the middle of the seal can also be provided between the inner surface of the box and the peripheral surface of the rotor, where the surfaces are tangent to each other alternately in the area in which they intersect with each other.

In order to minimize the wear on the blades and improve the operating time, sliding supports can be provided in the recesses in the rotor. The sliding bearings or bearings may be in the form of changeable bearings inserted or permanently provided in the rotor. In one embodiment, the peripheral surface of the rotor can intersect the inner surface of the box through a sector and then a corresponding recess is formed in the surface of the machine case. In one embodiment, the rotary piston machine comprises at least one compressor unit, which rotates together with the combustion machine unit and which has a design corresponding to the combustion machine unit, that is, a separate cavity, a separate rotor and separate blades, in addition to passages connecting the respective cavities. In order to stabilize the fixed axial rod in the box, the free end of the axial rod can be supported internally in the rotor itself by means of a normally designed eccentric adapter and support. DESCRIPTION OF THE DRAWINGS An exemplary embodiment of the rotary piston machine according to the invention will now be described in detail where it shows: FIGURE 1, a perspective view of a rotary piston machine in the form of a combustion machine and two adjacent compressors, one on each side of the combustion machine and thus appear in the assembled state; FIGURE 2 shows the rotary piston machine when one of the end covers is raised; FIGURE 3 shows the rotary piston machine according to Fig. 2, when the end bearing or bearing is removed; FIGURE 4 shows the rotary piston machine according to FIG. 3, when another part of the box is removed and more of the rotor appears; FIGURE 5 shows the rotary piston machine according to FIG. 4, when another part of the box is removed and more of the rotor appears; FIGURE 6 shows the rotary piston machine according to Fig. 5, when another part of the box is removed and more of the rotor appears; FIGURE 7 shows the rotary piston machine according to FIG. 6, wherein one of the halves of the rotor box is removed and the rotor blade unit appears clearly; FIGURE 8 shows the rotary piston machine according to FIG. 7, in which the rotor blade is removed so that the second half of the rotor case remains in the case, in addition to the axial rod provided eccentrically in the case. box; FIGURE 9 shows the rotary piston machine according to FIG. 8, in which the last rotor part is removed; FIGURE 10 shows the rotary piston machine when another part of the box is removed; FIGURE 11 shows the rotary piston machine when another part of the box is removed so that only the second end cover remains together with the eccentric shaft rod; FIGURE 12 shows the eccentric shaft rod; FIGURE 13 shows the assembled rotor blade unit including three blade parts; FIGURE 14 shows the unit according to FIG. 13, disassembled and the individual parts separated; FIGURE 15 shows one half of the rotor case viewed externally; FIGURE 16 shows the same half of the rotor case as in Fig. 15, but seen internally; FIGURE 17 shows the lower half of the rotor case seen internally; FIGURE 18 shows the lower half of the rotor case viewed externally; FIGURE 19 shows a main view of a second embodiment of a rotary piston machine in the form of a compressor or pump having four blades according to the invention; FIGURE 20 shows another embodiment of the rotary piston machine, according to the invention, having four blades wherein the peripheral surface of the rotor through a sector cuts the internal surface of the box; FIGURE 21 shows a main view of another embodiment of the rotary piston machine according to the invention, having a single blade; and FIGURE 22 shows the eccentric adapter that supports the rotor eccentrically with respect to the cavity of the box. DESCRIPTION DETAT-T'ar > a r,, THE INVENTION Fig. 1, shows a rotary piston machine , in one embodiment of the invention. However, it should be noted that in this embodiment of the machine that is assembled in a combustion machine unit and two compressor units, one on each side of the combustion machine unit and in which all. units rotate together. In addition, it should be noted that the machine is designed and manufactured with such precision that the use of seals or sealing is kept to a minimum. The use of labyrinth seals is considered. Other tests will show this over time and possibly at least some applications will work well without seals and without lubrication, except for the bearings that are sealed and pre-lubricated. Construction materials may have different grades of steel, but plastics and Teflon will be suitable for some applications. The rotary piston machine 10, in FIGS. 1-18, represents a supercharged combustion machine. The machine 10, comprises a box 5, which has several internal cylindrical surfaces surrounding a rotor 2, located eccentrically where the output power part of rotor 2, is shown in the figure, note that the machine has no crankshaft and power it is taken directly from the rotor 2. The rotor 2, rotated around an axis of rotation A, the box 5, is constructed of a number of plates having a similar thickness and similar external configuration. The box 5, on the other hand, can be manufactured in two halves that are placed against each other. However, as the box is manufactured, it is a selection that must be made with the technician. The rotary piston machine 10 comprises inlet passages 3 for fuel and air mixtures and outlet passages 4 for the exhaust gases. The individual parts with which the box 5 is constructed, are numbered 5a to 5g. Thus, the plate 5a represents the upper end cover and the plate 5g, the lower end cover. Fig. 2 shows the rotary piston machine according to Fig. 1, but the cover 5a is removed, here an upper end bearing 14 appears, internally of the end cover 5a, there is a circular opening recess to receive the support 14. The bearing 14 thus acts as an end support for the rotor 2. Fig. 3 shows the same as Fig. 2, except that the bearing bearing 14 is removed from the end of the rotor 2, thus more than rotor 2 appears. Fig. 4 shows the same as Fig. 3, but where another plate 5b of the box is removed, so more part of rotor 2 appears, and shows a rotor blade la. Also the internal passage 2, the internal passage 3 is shown, leads from the external machine box 5, to a chamber 9a, inside the box 5. That part of the rotor 2, has the blades the, and the box part 5c , which is illustrated in Fig. 4, and constitutes a first compressor unit that rotates about the axis A. In Fig. 5, another part 5c has been removed from the box 5, and more parts of the rotor 2 appear. a rotor blade Ib is shown, which runs in the chamber 9, and together with this rotor part 2, forms the combustion machine unit. From the chamber 9b, in the combustion machine unit an outlet passage 4, extends and leads to the environment. In Fig. 6, another plate part 5d is removed from the box 5 and appears in addition to the combustion unit. In Fig. 7, the upper half 2a of the rotor 2 is withdrawn, and the blade unit 1 with its respective blades the, Ib, appears clearly. The Alabe unit 1, comprises in the embodiment shown three compressor blades la, and three combustion blades Ib. Each blade, Ib, is hingedly connected to one end of control arm 7, which is at the other end pivotally supported on a rod 8, with a stationary axis having a central axis B, coinciding with the longitudinal axis of the box of machine 5. This is shown in its entirety in Figs. 8-12. The control arms 7, do not transmit any power, but for each blade the, ib, le, are in forced movement to slide radially inwardly and outwardly, in the guide recesses 11, in the rotor 2, so that the blade tips at any time during the rotation of rotor 2, are tangent to the internal surface of the box. Reference numeral 6 indicates an eccentric adapter that is described below with reference to Fig. 22. The other compressor unit is below the combustion engine and completely corresponds to the upper compressor unit.

In Fig. 8, the lower part 2b of the rotor 2 is shown after the blade unit 1 has been removed.

In this Fig. The recesses or grooves 11, which extend radially where the respective vanes run la, ib, le, are clearly shown. As mentioned the shaft shank 8, extends centrally in the cavity 9, of the box 5.

The axis A of the rotor 2 extends parallel to the central axis B, of the box 5, but they extend eccentrically with respect to the geometric axis B, of the box 5. This eccentricity is illustrated in Fig. 5, where both axes A and B are shown. By means of this eccentricity the radial movement or forced movement of the respective vanes la, ib, le, inwards and outwards in the respective recesses ll, in the rotor 2. Fig. 9, shows the cavity 9, in the machine box 5, after that the part 2b has been removed from the rotor 2. In Fig. 10, another part of the plate 5e is removed from the box. In Fig. 11, the final end cover is shown 5c, after the plate part 5f has been removed. Fig. 12 shows the stationary axle rod 8, fixed to a stationary end flange 15. Fig. 13 shows the blade unit 1, assembled when it is placed on the stationary axle rod 8. As mentioned Alabe unit 1, consists of a combustion machine blade IB, and two combustion machine blades, located on each side of the combustion machine blade IB. Each set of vanes la, ib, le, is articulated to respective control arms 7. When the vane unit 1, consists of three sets of vanes it is found convenient to arrange the respective control arms 7, with different mutual distances for each set of blades la, Ib, le, as shown in Fig. 14. Each control arm 7, includes a bearing 16, which allows the blade set la, ib, le, and each control arm 7, rotate around the stationary axle rod 8. In addition, each set of blades consists of an articulated connection in the form of an axle fork 17, having a rotational geometrical axis C, which is provided between the blade set la, ib, le , and two control arms 7. It should also be understood that in the optimum modality considered of the machine, there is a certain relationship between the thickness t, of each blade, the distance between the axis c, and the b, and the eccentricity of the rotor 2m, with respect to box 5 this is the distance between the axes s 1, b. This is necessary so that the tips of the blade are to be followed with a predetermined distance and a minimum light, the inner surface 20, of the box 5. In addition, the surface of the blade tips lbt must be curved so that the surface continuously follows or is tangent to the inner surface 20 of the box 5 in low light. The point of tangency is, however, displaced along the arcuate surface of the blade tip lbt and is realized as a rocket movement on the inner surface 20. In order to obtain that this corresponds to the surface of the tips of the blade. Alabe lbt have a center of curvature in the axis c, which joins the blade Ib to the control arm 7. This is more easily understood by studying Figs. 19-21. The same relationship as the one described above is also true for the compressor blades and the one that have their own thick separated distances, and curvature of the blade tips. The surfaces of the blade tips can be provided with a suitable sealing means for coupling the inner surface 20 of the box 5, however it is preferred that there be no contact between them, and thus a suitable solution can comprise labyrinth seals on the surface of the wing tips with the necessary extension and design. Fig. 15 shows the upper part 2a of the rotor 2, and what constitutes the stroke for the power output, while Fig. 16, shows the same inverted part so that the internal cavity and guide recesses, where the vanes of the upper compressor are sliding it radially inward and outward.

Fig. 17, shows the lower part 2b, of the rotor case 2, seen internally and Fig. 18, shows the same part seen externally and with the respective sliding recesses 11b, for the blades of the combustion machine Ib, and the sliding recesses lie, for the vanes, in the lower compressor unit. The operation of the machine will now be described with reference to Figs. 4-6. As indicated at the beginning the illustrated embodiment of the invention shows a combustion machine having a compressor unit on each side. The rotor 2 will be rotating around its central axis A in the direction of the arrow R indicated in Fig. 4. When the rotor 2 rotates, the compressor blades which are running in the compressor chamber 9b, take a mixture combustible air, through step 3, and introduce it to chamber 9b. The suction period begins when the vane passes the entrance to step 3, which leads to chamber 9b and lasts until the next vane passes the same entrance. That side of the compressor blade, which is opposite to the direction of rotation, constitutes the suction side of the compressor, while the side facing in the direction of rotation constitutes the pressure side. This implies that when the compressor vanes are passed through the entrance of the passages 3 to the chamber 9a, the pressure side of the compressor vane la begins its compression work, while the opposite side begins its suction work. Because the chamber 9a, which points on the inner surface 20, of the box converges towards the peripheral surface 21 of the rotor, a compression operation is achieved in a known manner when the vanes travel in the chamber 9a. In addition, passages are provided between the compressor chamber 9a, and the combustion chamber 9b, in the combustion engine and located adjacent to the compressor unit in the next layer, as moved in Fig. 5 and 6. Each step it extends from the narrowest part of the compressor chamber 9a, and opens in the combustion chamber 9b, where the chamber begins to expand and forms together with the vanes 9b, an expansion chamber. The step or steps may be located in suitable places, such as in the body of the machine case 5, or in the rotor where the rotor blades la, Ib, act as valves to carry the fuel mixture at the correct time. In Fig. 6, it is the outlet of the passage from the compressor chamber 9c, to the combustion chamber 9b, indicated by the figure 12. A corresponding outlet is provided through the box 5, from the upper compression chamber 9a , but it is not shown in the drawings. The output, however, communicate with smaller recesses 18, in the rotor 2, for an instantaneous transfer of pressure from the compression chamber 9a, to the combustion chamber 9b. Thus the outputs 12 and the recesses act as valves with respect to each other. The fuel mixture is ignited approximately in the area in which the recess 18 is, in Fig. 6, and occurs when the alabe ib approaches this place. When the rotor 2, and the blades Ib, have passed through a certain circle arc corresponding to the expansion phase, step 4, for the exit or exhaution is exposed and the exhaution product leaves the environment. As understood, the fuel air mixture is supplied to the combustion machine unit, that is from the upper and lower compressor. In both modes, there may be a single compressor unit, an external compressor unit, or a complete omission. The numbers of blade sets may vary according to what is considered appropriate for the respective application. Fig. 19 shows a 4-blade compressor embodiment of the present invention. As in the described embodiment, this includes a schematically illustrated case 5, a rotor 2, but 4 blades i, which move radially outwardly and inwardly in the sliding recesses ll., placed in the recess of the rotor 2. The box 5, has a cavity 9, centered on the axis b, and an internal surface 20, which almost touch the end surfaces of the blades 1. The rotor 2, has a surface peripheral peripheral 21, and rotates about the axis of the rotor A. Between the positions C and D, there is the internal surface 20, and the box 5, described by a sector of cylindrical surface corresponding to a sector of the peripheral surface 21, of the rotor 2. Thus the entire inner surface of the box can be described as being formed of two incomplete cylindrical surfaces, or sectors of cylindrical surfaces having no coincident central axis and wherein the smaller cylindrical surface cuts into the larger cylindrical surface through a predetermined cylinder sector. The place (C and D) where the two cylindrical surfaces intersect a type of valves are formed that effectively stop the backward flow of the gases. Optionally, labyrinth seals can be provided in box 5, in area C and D, possibly in the entire area between C and D. The distance between C and D, can be varied or improved for the respective application of the machine. When the distance between C and D is zero, the inner surface of the box 5 will be cylindrical and the peripheral surface 21 of the rotor 2 will be tangent to the inner surface 20, along a line at the location C, D. When the rotor rotates in the direction of the arrow R, air is sucked through the inlet passage I. The next blade 1, carries the air pulled and begins the compression work when the blade 1, is passing its lowest position (6 clock hours in Fig. 19). The air is compressed against the outlet passage U, by the rear movement of the vane 1, towards the uppermost position (12 clock hours in Fig. 19). Fig. 20 shows a 4-blade rotary machine, here in the form of only one pump or one compressor. The machine is very similar to the compressor described above with reference to Fig. 19. However, now the eccentricity and those circles (cylindrical surfaces) intersecting each other appear more clearly. The rotor 2 moves in the direction of the arrow R, the air sucked through the inlet passage I, the air is pulled and dragged by the blades and is moved again through the opening U. FIG. 21 shows a rotary blade machine, here in the form of a pump or compressor unit which also has optional sealing means 23, and bearings 22, the sealing means may be simple scraping seals or labyrinth seals. In the holder 22, it can be inserted made of a suitable support material, such as babbit or bronze metal, possibly teflon for some applications. The blade tip can also be provided with a seal 24, which contacts or scrapes against the surface 20 'of the box. Between the input I, and the outlet U, a seal 28 is advantageously placed, preferably a labyrinth seal. A revolving machine of a blade needs counterweights (not shown in order to balance the forces of mass). Fig. 21, illustrates in particular the geometric relationships that are applied for an optimal machine. An optimum machine is defined as a machine that has a minimum of coupling seals and preferably is totally lacking contact seals. However, non-contact stamps such as labyrinth seals are also acceptable. Each wing tip describes a cylindrical surface sector having a particular arc length and curvature which are determined on the basis of geometric relationships. The radius of curvature R4 of the blade tip is determined by the distance from the axis C to the inner surface 20 'of the box 5. The thickness t of the blade and thus the arc length of the cylindrical surface determined by the distance between the central axis B and the axis C, according to the pivot radius R3, for the C axis, and the distance d, between the axis of the rotor A and the central axis B. As shown in the figure, the dotted blade is also seen in the straight down position, the tip of the blade performs a rolling movement against the internal surface 20 ', of the box 5, during its revolution with the rotor 2. At the middle of the rotor revolution 2, the blade tip has made a rolling motion between the end edges of the arc, so the blade tip is rolling backwards and forward once in each revolution of the rotor. The thickness t, of the alabe can be greater than the optimum without having great importance. However, if it is thinner the tip of the blade will no longer be at all times tangent to the surface 20 'during one revolution of the rotor and will therefore provide distance and light between the surface 20' and the tip of the blade. Fig. 22 shows in more detail the eccentric adapter 6. The eccentric adapter 6 is fixed non-rotatably to the shaft of the axle 8, by means of a key 25. The adapter 6 has an eccentric with respect to the central axis B, and a cylindrical support fork 26, which supports a bearing 27, which is located eccentrically with respect to the central axis B, but is centrally located with respect to the axis of the rotor A. The bearing 27, stabilizes the axial rod 8, at the end free of it, in addition to providing internal support to the upper rotor part 2a. Therefore, the bearing is located concentrically with respect to the upper external support 14, and a corresponding bearing (not shown) at the opposite end of the rotor, that is, supports the part of the rotor 2b, this eccentricity provides the forced movement of the blades 1, by means of the control arms 7.

Claims (9)

1. NOVELTY OF THE INVENTION Having described the invention as above, property is claimed as contained in the following: CLAIMS 1. - A rotary piston machine comprises a box having a cavity, a rotor received in the box, rotor having an axis rotary and a peripheral surface, inlet and outlet passages in communication with the cavity, one or more radially extending vanes slidably received in recesses in the rotor, each vane extends radially from the inner surface of the box to the axis of the rotor, and at least one working chamber is part of the cavity and is defined by the internal surface of the box, the peripheral surface of the rotor and the lateral surface of at least one blade, in each blade being hinged in connection about a axis at one end of a control arm and at the other end is pivotally supported on a shaft with a fixed axis having a central axis coinciding with the axis which extends centrally through the cavity of the box, which axis extends in parallel with and spaced from the rotor axis, and the rotor itself constitutes the unit for the intake or power input, characterized in that, each blade tip describes a cylindrical surface sector having a center of curvature on the shaft extending through the joint connecting the blade to the control arm.
2. 2. - A rotary piston machine according to claim 1, characterized in that the length of the cylindrical surface sector and thus the thickness of each blade is determined by geometric relationships, that is, the radius of curvature for the surface sector cylindrical, the distance between the rotor axis and the central axis.
3. 3. - A rotary piston machine according to claims 1, 2, characterized in that, the sealing means is provided between the blade tip and the internal surface of the box.
4. 4. - A rotary piston machine according to claims 1, 3, characterized in that the sealing means are provided between the blade recesses and at least one of the side surfaces of the blades.
5. 5. - A rotary piston machine according to claims 1, 4, characterized in that the sealing means are provided between the internal surface of the box and the peripheral surface of the rotor, where the surfaces are tangent to each other.
6. 6. - A rotary piston machine according to claims 1, 5, characterized in that the blade recesses comprise sliding bearings that coact with the blade.
7. 7. - A rotary piston machine according to claims i, 6, characterized in that the peripheral surface of the rotor through a sector intersects on the internal surface of the box and a corresponding recess is formed on the internal surface of the box. machine box.
8. 8. - A rotary piston machine according to claims 1, 7, characterized in that the machine comprises at least one compressor unit that rotates together with and corresponds to the combustion machine unit and has a separate chamber, a separate rotor and separate blades, and steps connecting the respective cavities.
9. 9. - A rotary piston machine according to claims 1, 8, characterized in that the fixed shaft rod is supported and stabilized at the free end thereof by a rotor, by means of an eccentric adapter.