HUT50934A - Rotary-piston machine particularly internal combustion engine - Google Patents

Abstract

The engine comprises a disk-shaped rotor (1) mounted on supports (3) in a casing (4) having a cylindrical and end-face walls (6, 7, 8). The end-face walls (7, 8) are provided with sector-shaped protrusions which form, together with the end-face surfaces (13a, 13b) of the rotor (1), the zones of compression, combustion and expansion connected, respectively, to a means (15) for feeding at least one component of the fuel mixture, to a means (19) for excitation of combustion and to a means for removing the exhaust gases. The rotor (1) is provided with radial slots in which are mounted laminated pistons dividing the zones into chambers of variable volume, whereas the end-face surfaces (13a, 13b) of the rotor (1), situated between the pistons, are provided with protrusions (23). The means (19) for excitation of combustion is mounted inside an annular zone coaxially oriented in relation to the axis (O1-O1) of rotation of the rotor (1) and limited by the lower and upper edges of the protrusions (23). The central angle, inside which is located the protrusion (23), is smaller than the central angle between the flat areas of the end-face walls (7, 8) of the casing (4).

Description

The present invention relates to a rotary piston machine which can be used mainly as a rotary piston engine. _

At present, due to very high levels of environmental pollution, the requirement for the design of internal combustion engines to be optimized for ecological, economic and technological characteristics, the layout, operating parameters and other features of internal combustion engines can be improved in a complex way.

A significant development in this regard is the rotary piston engine, which has a size of about 1.5-2 times smaller than conventional alternator piston internal combustion engines, has about half the number of parts to be installed and is considerably simpler to manufacture. In addition, the rotary piston engine is distinguished by the fact that its mechanical efficiency is significantly better and that the amount of nitrogen oxides released into the ambient air by the exhaust gases is significantly lower than with conventional engines.

In addition, known rotary piston machines have a relatively high heat loss due to the specific surface design of the combustion chamber and the expansion chambers. This, in turn, means that the efficiency is slightly below the desired value and the specific fuel consumption is relatively high.

For example, a rotary piston engine having a cylindrical housing is known from Polish Patent 38'112.

The inside of the house has a cylindrical working space, which is bordered by a cylindrical shell wall and front panels. In the house the hen • ·

- A rotor bearing rotatably mounted coaxially with a 3-groove jacket wall. Each end face of the housing is provided with sector-shaped recesses which are evenly distributed along the periphery. Each of these recesses has a flat bottom which is parallel to the flat sections of the front of the housing, and the profiled surfaces are connected thereto. Between the sector-shaped recesses, an ignition unit, such as an electric spark plug, is arranged on the front face of the housing. Between both housing faces and the rotor face there are provided sector-shaped compression and expansion sections and combustion sections which are located behind the compression sections in the rotational direction of the rotor.

It is provided with radial grooves extending along the face of the rotor, in which axially displaceable plate-like pistons are arranged. These pistons cooperate with their front faces with the front faces of the housing and divide the sector-shaped sections into separate and variable-volume chambers. To reduce frictional resistance during piston movement, the pistons are arranged in ball bearings.

The housing includes at least one fuel component inlet assembly associated with the compression section. Further, the exhaust gases have an outlet unit associated with the expansion stage. In order to cool the motor housing, cavities are formed on the front sides of the housing, which are connected to the refrigerant source.

One feature of the above rotary piston engine is that the sector-shaped chambers are groove-like.

• ·

- 4 As the rotor is rotated, the combustible fuel mixture enters the compression chamber. The piston then conveys the combustible mixture to the combustion chamber, where it is lit by the spark plugs, i.e. combustion occurs. During transfer to the expansion stage, the gases exert pressure on the flat piston edges protruding from the rotor, thereby generating the torque of the rotor, which is then passed through the rotor axis to the driven unit, i.e. the consumer.

The mixture is thus incinerated in a groove-like combustion chamber which is characterized by having a relatively large heat release surface and a relatively small volume due to the particular design of the chamber wall. Thus, relatively large heat losses occur on the housing and rotor front faces, while the combustion mixture flows in a straight line in the slot, thus providing little homogeneous mixing, which would be desirable. Therefore, since the available turbolence in the combustion mixture is extremely low, combustion of the combustion mixture can be considered to be imperfect. This has the disadvantage that the specific fuel consumption is too high, the carbon monoxide content in the exhaust gases is increased, and the excessively unburnt hydrocarbon components are present in too high a proportion with other toxic gases. A further disadvantage is that the above combustion process also involves strong formation of coke and severe wear of the sheet-like pistons is to be expected.

Experience with the above engine also requires very high noise loads, which can be explained by the fact that some parts of the slot-shaped combustion chamber are located at a relatively large distance from the spark plug, so that there is no uniformity.

- 5 temperature conditions. This limits the degree of compaction of the combustible mixture, reduces the effective efficiency and presupposes the use of high-octane and expensive fuels. In explosion mode, engine power drops rapidly, but maximum temperatures and pressures increase rapidly, resulting in rapid wear and damage to the piston.

The above engine design can also be used in Diesel mode or Otto engine mode with petrol injection, however, whereby mixing with combustion air must occur throughout the volume of the groove-like combustion chamber, where, however. rather unfavorable in relatively narrow gaps (o, 4 to o, 8 mm).

In the above rotary piston engine, some of the leaf-like piston surfaces extend beyond the rotor face during combustion mapping and are exposed to very high temperatures (25 to 2700 K) and pressure (3 to 10 MPa) released during combustion of the mixture, thus providing intensive cooling. required. However, the rotary piston engine described above does not, however, employ any cooling to the flat piston and rotor surfaces mentioned, nor does it have a forced lubrication system, which results in a very limited engine life.

A further disadvantage of the above solution is that the arrangement of the plate-like pistons in the ball bearings further increases the total weight of the moving elements, resulting in an undesirable increase in the collision pressure of the plate-like pistons on the housing faces.

It is an object of the present invention to overcome the above shortcomings, that is, to provide an improved solution which substantially increases the efficiency of the rotary piston machine, especially an internal combustion engine, and at the same time reduces the surface to volume ratio of the combustion section.

In order to solve this problem, we started with a rotary piston engine of the type mentioned in the introduction, the rotor of which is rotatably mounted in a housing, the housing has a cylindrical working space which accommodates the rotor and cylindrical wall and front faces; sector-shaped recesses each having a flat bottom plate which is parallel to and flat through the profiled surfaces of the housing front face, and having an ignition device arranged between the sector recesses with a flat portion of the front face of the housing face together forming sector-shaped sections: a compression section which is connected to an inlet unit for at least one component of the combustion mixture; an expansion section associated with the exhaust outlet unit; a combustion section extending downstream of the compression section in the direction of rotation of the rotor and having uniformly distributed continuous radial grooves in which sheet-like pistons are displaceable axially, and the end faces of the pistons cooperate with the housing front walls and the sector-shaped sections The invention, that is to say, the essence of the invention, is that recesses are formed in the rotor end faces between the flat pistons, and that the ignition devices are arranged in a ring-like section which is concentric with the rotor axis of rotation. has a lower recess distal to the rotor periphery and an upper recess peripheral to the rotor periphery, and the central angle of this recess is smaller than the flat sections of the front sides of the housing measurable central angle.

By designing the recesses on the rotor face surfaces, it is possible to minimize the gap between the housing and the rotor face faces. As a result, the slot-shaped combustion chamber is eliminated and the combustion process is allowed to proceed in the recesses as detailed above, since practically all of the combustion mixture enters these recesses after compaction. This is where the combustion mixture is ignited and burned.

Thanks to the above measures, the ratio of the surface area of the recess formed on the face of the rotor, which in fact acts as a combustion chamber for combustion of the combustion mixture, is much smaller than the ratio of surface to volume of the slot-like combustion chamber. In this way, heat losses are significantly reduced and at the same time it is possible for the combustion mixture to flow turbolically at the end of the compression stroke. This accelerates the combustion process of the combustion mixture, achieves a more perfect combustion and consequently improves engine efficiency.

Because of the relatively short distance to each point of the recess in the present invention, the combustion mixture is primarily ignited in the recess, i.e., in the zone of maximum combustion chamber temperature. Subsequently, the combustion process extends to a negligible extent in the direction of the gap, that is, in the area of the relatively cold wall surface. This minimizes the risk of detonation, increases the degree of compression and, consequently, improves the effective efficiency of the engine.

By designing the recess within a certain central angle, which is smaller than the central angle of the flat surfaces of the housing front walls, it is possible to reduce the specific fuel consumption and at the same time increase the effective efficiency of the engine.

According to a further feature of the present invention, the clearance between the rotor and the front walls of the housing is advantageously selected to be between 0.1 and 0.3 mm.

By the aforementioned measure, the volume of the gap between the rotor and the housing walls is minimized, thereby practically eliminating the possibility of the mixture burning, and consequently greatly reducing the heat loss to the rotor and housing walls through the cooling system.

Furthermore, when reducing the gap between the flat sections of the rotor face surfaces and the housing face faces, it is advisable to select it greater than o, o mm, within the specified range, since these surfaces will inevitably fail due to thermal loading or mechanical deformation

- 9 resulting in friction.

According to the invention, if said gap were to be larger than 0.3 mm, the volume would be significantly increased, which would be combined with the undesirable effects already described above. Such an undesirable consequence would be incomplete combustion of the combustion mixture, since a gap of this size would have too large heat release surfaces on the walls. Thus, the flat housing wall sections and the protruding sheet piston portions would force the combustion mixture into a flat flow due to the high heat loss of the rotor face surfaces, which would adversely affect the mix preparation. Poor turbulence in the combustion mixture, as noted above, would result in incomplete combustion of the combustion mixture. This would also result in higher specific fuel consumption, increased carbon monoxide and other toxic component content in the exhaust gas, and enhanced coke formation and increased piston wear.

According to a further feature of the invention, the recess wall is at least partially formed as a rotating surface.

By designing such a recess, the ratio of recess surface to volume is minimized, heat losses in the cooling system can be minimized, and the flow of the combustion mixture into the recess at the end of the compression stroke can be improved, and the gases at the start of the expansion stride. A further advantage is that this eliminates the formation of stagnant or "clogging" zones, results in a more efficient and intimate mixing of the combustion mixture and consequently further improves fuel combustion.

According to a further feature of the present invention, it is desirable to provide a separate unit that prevents gaseous media from flowing between variable volume chambers. This unit can be arranged between the cylindrical wall of the housing and the rotor and connected to the rotor so that it is in contact with the housing end walls.

This latter measure minimizes the risk of gaseous fluid flow between the chambers and thus further improves engine efficiency.

The unit for preventing the flow of gaseous media between the chambers can be, for example, a ring arranged on the circumference of the rotor and rigidly connected to the rotor. It is desirable to have a series of grooves on the annular edge opposite the cylindrical housing surface. Advantageously, a recess housing which is concentric with the ring and is rigidly fixed to the cylindrical wall of the housing may be used. This casing, together with the grooves, forms a labyrinth seal.

The flow of gaseous media between the chambers can thus be prevented by the above measures, so that by incorporating a high resistance in the direction of flow of the flowing gases, the gap loss of the gases is effectively reduced. Practical engine construction has shown that a labyrinth seal can be formed for very small gaps, for example by applying a graphite-aluminum coating to the correct ring or other suitable coating. The minimal gap is made possible by the fact that such a coating is sufficiently soft and that the labyrinth protrusions can cut into the grooves themselves. Such labyrinth seals have little resistance to the frictional forces of known, contacting seals.

Using the labyrinth seal of the invention extends the life of the motor. A ring disposed in the periphery of the rotor and rigidly coupled to the rotor prevents the plate-like pistons from contacting the cylindrical wall of the housing where otherwise the peripheral speeds and mass forces acting on the piston pistons would be very high. Due to the ring according to the invention, the plate-like pistons, which perform an alternating movement in the axial direction, slide on the inner surface of the ring at a considerably lower speed than the circumferential speed measured on the outer diameter of the rotor. Thereby, the bumping of the surface of the sheet-like piston is effectively reduced. Furthermore, it has also been possible to center the plate-like pistons by their side surfaces, thereby eliminating tension of the plates. Because plate-like pistons are most abrasive at the outer diameter, where higher linear velocities are to be expected while contacting the housing walls at a smaller diameter, gas-hydro-dynamic sealing, which also acts as a bearing, begins to work effectively in the resulting gap. loads. This results in longer life of the plate-like pistons.

It is preferable that the ring is provided with an annular collecting channel on the outer surface of the ring which is connected to the radial channels of the rotor through a channel formed in the ring. These, in turn, are connected to the through radial grooves and the axial channel formed in the rotor. Further, the axial channel is connected to a lubricant source, which through an outlet channel is provided to the annular collecting channel.

- Connected to 12 nations.

The above design ensures that the friction surfaces are continuously supplied with lubricant during operation, while the friction surfaces can be permanently cleaned by removing residues from wear and reducing wear losses. At the same time, the wear of the leaf-like pistons slows down significantly on both the lateral and frontal surfaces. This is due to the effective cooling of the high-heat elements of the rotary piston engine, which is clearly provided by the above arrangement. On the other hand, due to the hydrodynamic seal used, the flow of gaseous medium between the chambers of variable volume can be completely eliminated. In addition, the above-mentioned embodiment of the gas-flow blocking unit also achieves the fact that in combination with the rotor channel system, no additional pump need be used for lubrication and cooling, since the rotor itself may substitute the functions of the transport pump through its radial channels.

The invention will now be described in more detail with reference to the accompanying drawings, in which an exemplary embodiment of the present invention is illustrated.

In the drawing:

Figure 1 is a longitudinal sectional view of the rotary piston engine of the present invention;

Figure 2 is a sectional view taken along line II-II in Figure 1;

Figure 3 is a sectional view taken along line III-III in Figure 1;

FIG. Figures 1 to 4 are perspective views of a rotary piston engine of the housing, namely the housing front wall;

Figure 5 is a side view of a flat piston of a rotary piston machine according to the invention;

Figure 6 is a sectional view taken along line VI-VI in Figure 5;

Figure 7 illustrates a lossless cycle diagram of a rotary piston engine of the present invention with heat input at constant volume at p-V coordinates;

- a Θ. Fig. 2A is a sectional view illustrating an embodiment of a fusing unit;

9 illustrates a further example of a nozzle fuse unit. its export form is shown;

Figure 10 is a loss-free cycle diagram of a compression ignition rotary piston engine with heat input at constant volume and constant pressures;

Fig. 11 shows a lossless ciliary diagram of a heat-driven internal combustion engine at constant pressure with ρ-V coordinates.

As shown in Figure 1, the rotary internal combustion piston engine of the present invention, which in this case operates according to the Otto cycle, has a disc-shaped rotor 1 which is disposed on a shaft 2 and is rotatably mounted in a housing 4 by bearings. The housing 4 has a cylindrical working space 5 which accommodates the disc-shaped rotor 1 and which is cylindrical with a wall 6 and 7, respectively.

- Bordered by 14 8 front walls.

Figure 2 shows that each of the front walls 7 and 8 is provided with sector-like depressions 9a, 9b, 9c and 9d, which are uniformly distributed around the circumference. Each of the depressions 9a, 9b, 9c, and 9d has a flat loa, lob, loc, or bullet bottom which is connected to and planarly profiled surfaces 12 of the front portions 7 and 8 of the housing 4 and 8, respectively. The sector-like depressions 9a, 9b, 9c and 9d in the front walls 7 and 8 form sections in alternating order with the face surfaces 13a and 13b of the rotor 1, namely: compression sections A 1 and A 2, combustion and B2 sections, expansion and C 2 sections as well as dividers and D2 sections.

The compression sections A-1 and A 2 are associated with inlet control units 14 and 15, respectively, for supplying at least one of the blend components. This relationship is in the initial region of sections A ^ and A2 (Fig. 2).

The expansion sections C 1 and C 2, in their final region, are associated with outlet control units 16 and 17, respectively.

In the planar sections 11a and 11c of the front walls 7 and 8 of the housing 4 there are arranged ignition units 18 and 19 which are in contact with the combustion sections B1 and B2 respectively.

Rotor 1 is provided with uniformly distributed, through-radial grooves 20o in which plate-like pistons 21 are displaceable axially. The end face of the pistons 21 cooperates with the end walls 7 and 8, respectively. The sheet-like pistons 21 divide the sections A A2 A2, Bj, B, C pC 2 ₅ 0 0 p 2 into separate chambers 22 whose volume varies. In the end faces 13 of the rotor 1, recesses 23 are formed between the plate-like pistons (Fig. 1).

The walls of the recesses 23 are at least partially preferably rotational surfaces. In the illustrated case, the recesses 23 are formed as spherical details.

According to the invention, the ignition units 18 and 19 are arranged in an annular region which is concentric with the center of rotation of the rotor 1 and is bounded by an outer edge on the rotational axis side and an outer periphery. In the exemplary embodiment shown, the ignition units 18 and 19 are configured as spark plugs 18a and 19a, respectively.

The recesses 23 according to the invention are designed such that their central angle (Fig. 3) is smaller than the central angle of the flat sections 11a, 11b, 11c and 11d of the housing 4 and the front walls 8.

According to the invention, the gap between the rotor 1 and the front walls 7 and 8 of the housing 4 is to be chosen between 0, 3 and 3 mm.

In the present case, this gap was chosen to be 0.1 mm. It should be noted that in Fig. 2, the face faces of the rotor 1 are designated 13a and 13b, respectively.

In addition, a rotary piston engine of the present invention is provided with a unit designed to prevent the flow of gas between chambers 22 of variable volume.

The unit 24 is disposed between the cylindrical wall 6 of the housing 4 and the rotor 1, connected to the rotor 1 and in contact with the front walls 7 and 8 of the housing 4.

In the present case, the flow prevention unit 24 has a ring 25, which in the illustrated case is disposed on the periphery of the rotor 1 and is rigidly connected therewith. Also, at 24 units

- 16 has 26 casings. At the edge 6 of the cylindrical wall 6 of the housing 4, the ring is provided with a series of grooves 27. The housing 26 is concentric with the ring 25 and is rigidly fixed to the cylindrical wall 6 of the housing 4. The ring 25 together with the grooves 27 forms a labyrinth seal. In order to reduce the gap to almost zero, the casing 26 is formed of a relatively soft material, such as graphite aluminum.

In order to properly lubricate the frictional surfaces, the rotor 1 is provided with an axial channel 28 and a radial channel 29 which connects the axial channel 28 with the through radial grooves 20o, in which, as mentioned above, the plate-like pistons 21 are arranged.

An annular groove 3o is ^{formed in} the cylindrical wall 6 of the housing 4 and on the outer surface of the ring 25 for cooling the rotor 1 and the plate-like pistons 21, and for forced lubrication and cleaning thereof.

The collecting channel 3o is connected via the channel 31 formed in the ring 25 to the radial channels 29 of the rotor 1. The radial channels 29, in turn, communicate with the radial grooves 2o. Furthermore, the axial channel 28 and the annular collecting channel 3o are connected via a drain channel 32 (FIG. 3) to a lubricant source not shown in the drawing.

The rotor 1 is provided with seals 34 which are intended to prevent gas penetration into the lubricant • · «* * · * '* ··

- system 33 (Fig. 1) of the system 17, on the other hand to cool the housing 4 and to allow the oil to enter the cylindrical working space 5.

In the exemplary embodiment shown, the front walls 7 and 3 are held together by screws 35.

In general, the weight of the plate-like pistons 21 should be kept to a minimum, be abrasion and heat resistant and provide a reliable seal for the various volume chambers. In view of the above requirements, in the embodiment of Figure 5, the sheet-like pistons 21 are formed of three sheets, such that the sheets 36a, 36b, 36c can be relatively slid relative to one another. The middle panel 36c is provided with resilient sealing members 37a and 37b. This makes it possible for the contact pressure of any of the side panels 36a and 36b and the contact pressure of the resilient sealing members 37a and 37b on the front walls 7 and 8 of the housing 4 to be up to a third of the known solutions. As a result, the service life is significantly extended, not sealing along a linear surface (as with the Wankel engine), but through a linear surface on the harrow. A further advantage of the above arrangement is that the sealing of the radial gap is improved and the loss of gas at the plate-like pistons 21 is minimized.

The operation of the rotary piston engine according to the invention is as follows:

The rotor 1 is rotated in the direction of arrow E in Fig. 2. In this case, the combustible mixture passes through the inlet control units 14 and 15 (or at least one of the mixture components) into the compression stages A ₁ and A ₂ respectively. The combustible mixture is then enclosed in the chambers 22, i.e. compressed in the compression stages A ^, A ₂ and introduced into the recesses 23 for passage. In the recesses 23, the combustion mixture is forced to intense turbolic motion at the end of the compression stroke.

At the moment of passage through the recesses 23, the compressed combustible mixture is collected in the combustion stages 8 through the ignition unit 18 and 19 and incinerated while maintaining a constant volume of the recesses 23.

The gases are expanded during passage into the expansion sections C1, C2 through the recesses 23. The expanding gases act on the piston portions protruding from the rotor 1 and thereby generate the torque of the rotor 1. The rotor 1 delivers the resulting torque through the shaft 2 to the clamp.

The gases are discharged from the plate-like piston 21, the expansion and C £ sections through the outlet control units 16 and 17, which are located at the end of the and sections.

The engine operating diagram described above is illustrated in Figure 7, with heat input and constant volume. In Fig. 7, the volume (V) for the horizontal axis and the pressure values (p) for the vertical axis are plotted. It is clear from the diagram that adiabatic condensation is carried out on section 1-f, in compression stages A ^ and A £.

Digar sections marked with fg points are isochore (i.e., constant volume) heat transfer (ql) in the burn sections B ^, 82. In addition, adiabatic gas expansion occurs in the gh-labeled section of the graph in the expansion Cy, C ₂ sections. In addition, in the hl section of the curve, the isochor cools the combustion gases with q2 heat output (exhaust gas is expelled by the flap-like pistons 21). through the discharge control units 16 and 17).

It should be noted that since the rotor 1 is arranged in the housing 4 with minimal clearance (the gap between the front faces 13a, 13b of the rotor 1 and the front walls 7 and 8 of the housing 4 is to be chosen according to the invention the hot exhaust gases do not affect the protruding portions of the plate-like pistons 21 until they exit the expansion C2. This, in turn, means less heat load for the plate-like pistons 21.

The rotary piston engine described above is to be considered as exemplary only, but is not intended to limit the scope of the present invention. Many other variants and improved embodiments of the invention are possible within the scope of the claims. The following is a further example of a rotary piston engine according to the invention. which operates according to a mixed heat supply cycle. The design of this rotary piston engine is substantially the same as the above Otto cycle engine. The only difference is that the ignition units 18 and 19 are formed as nozzles 18g, 19g (Fig. 8), or nozzle plugs 18c, 19c are arranged one after the other in the direction of rotation of the rotor 1 (Fig. 9).

The 18c, 19c nozzle plugs allow the fuel components (fuel) to be injected and also reliably ignited. However, the nozzles 18b and 19b are only suitable for fuel injection. The inlet regulator 14 and 5 15 units in this case the combustion mixture at least • · ·

20 components of a component thereof, in this case the component is the oxidizing agent, i.e. air. Such an engine has an even higher rated efficiency.

The rotary piston internal combustion engine of the present invention can also be run on dense hydrocarbon fuels, but at lower speeds. The lossless thermodynamic duty cycle for such an engine is shown in lo. with mixed heat supply.

As a lo. As shown in FIG. 4A, the m-n curve illustrates adiabatic compression, namely air compression, in compression A? Meanwhile, during the compaction process, the air used as the oxidation medium is heated up, that is, to a temperature value at which the fuel injected through the nozzles 18b, 19b and 18c, 19c spontaneously ignites.

In the curve sections n-b, ql of heat is supplied to the combustion mixture by the constant volume charge in the combustion sections B1, B2. On the o-p curve, the amount of heat ql '' is added to the combustion mixture by post-combustion of the combustion mixture in the expansion stages cl, c2. The p-r curve illustrates the adiabatic expansion in the expansion cl, c2. Further, the r-m curve illustrates an isochor gas quench section by releasing heat q2 '(this amount of heat exiting the engine through exhaust control units 16, 17 through the exhaust gases).

Hereinafter, the rotary piston engine of the present invention will be a diesel example. embodiment.

• · * ··· ·· · · · · ·

The structural design of the rotary piston engine is essentially the same as described above. The difference is with the higher rotor speeds of the rotary piston engine operating on the Diesel cycle and the use of a mixed dosing cycle in a manner known per se.

Figure 11 shows a loss-free cycle diagram of such a rotary piston engine where the heat is supplied at constant pressure. Again, the volume (V) was applied to the horizontal coordinate axis and the pressure (p) to the vertical coordinate axis.

As shown in Fig. 1, the section i-j in the diagram shows the adiabatic compression of air in the compression section A |, A £. During this compaction, the air used as an oxidizing agent heats up and even reaches a temperature at which

for example / diesel oil spontaneously ignites.

The section marked j-k represents the isobaric heat input (the amount of heat indicated by ql '' ') is all done in the combustion Bp B2 and in the expansion Cp C2. Further, the section labeled k-1 represents the adiabatic expansion of the gases in the expansion Cp C2 section. Finally, section 1-i represents the isochoric cooling of the combustion products by releasing q2 '' of heat (this amount of heat leaving the engine through the exhaust units 16, 17).

An important advantage of the internal combustion engine according to the invention is that, in the latest embodiment, the fuel injected into the recesses 23 is not able to leave it under centrifugal force, as can be the case with known rotary piston machines ( · ·· «·· ··

22, which is perpendicular to the centrifugal force vector), however, according to the present invention, this introduction into the recesses takes place under optimum conditions (with the possibility of post-combustion in the expansion C 1 -C 2, which achieves even more perfect fuel combustion).

The above-described construction of the rotary piston engine of the present invention relates specifically to an internal combustion engine which operates on the principle of combustion of the combustible mixture. However, the rotary piston machine can be operated with steam, compressed air, or other working fluid and can be used as a pump or compressor. For this purpose, the compression and expansion chambers must be provided with inlet and outlet holes along with other units on their profiled surface sections.

All in all, the recesses 23 have the following advantages for the internal combustion engine by designing a combustion chamber as a surface of rotation body:

- The heat loss to the cooling system can be greatly reduced;

The thermal load of the sheet-like pistons 21 has been significantly reduced;

- Improved fuel combustion;

- Improved indicated engine efficiency;

- We have significantly reduced emissions of pollutants to the outside air, ie flue gas emissions.

The ring 25 arranged on the cylindrical outer surface of the rotor has the following advantages:

- The flow of gas between chambers by the various sealing elements ♦ * · • 4 · · ♦ ·· · ♦ ·

- reduced to the outer surfaces of the ring due to its 23 application;

- The reliable cooling and lubrication system ensures good cooling and lubrication for all high-temperature structural components, while allowing the rotor to perform the function of the pump;

By extending intensive cooling and lubrication and preventing contact with the housing wall, the life of the plate-like piston 21 is significantly increased. We also provide new sealing options.

The rotary piston machine of the present invention offers a wide range of applications for the use of ceramic or fiber reinforced components and for the introduction of waste-free manufacturing techniques in the manufacture of engine parts.

Depending on the work cycle chosen and the materials used, the effective efficiency of the present invention may range from 28% to 55%.

The widespread application of the present invention provides an originally novel and highly efficient rotary piston machine or internal combustion engine, which differs significantly from the conventional Wankel engine in the following:

- Simpler construction and fabricability;

In terms of size and rotor weight, the engine according to the invention is 1.5 to twice smaller than the Wankel engine;

Manufacturing and operating costs are 1.5 to 3 times lower than the present invention;

- Its noise level is significantly lower;

- Dynamically easy to balance, eliminating the need for a separate damping system;

• ··· * ·· · * • «* · · ·

- Higher and more even torque at lower rpm, providing excellent conditions for widespread use of automatic transmissions;

- Can run on a wide variety of liquid fuels and lower quality gaseous fuels, further reducing operating costs.

Combined with the environmental benefits detailed above, these advantages open up a wide application of the rotary piston machine of the present invention.

Finally, it is noted that the rotary piston machine of the present invention is advantageously used in passenger and lorries, commercial vehicles, aircraft, ships, agricultural machinery, and any other area of practical life where an economical, compact and low-noise internal combustion engine requires up to 100 kW. along with pollution.

Claims (6)

PATENT CLAIMS A rotary piston machine, in particular an internal combustion engine having a rotor (1), which is rotatably mounted in bearings (3) of the housing (4), wherein the housing (4) has a cylindrical working space (5), said rotor (1). ) receiving and delimiting cylindrical walls (6) and front walls (7, 8), furthermore, the front walls (7, 8) are provided with sector-like recesses (9a, 9b, 9c, 9d), each having a flat bottom (loa, lob). , loc, sphere), which is connected to the planar sections (11a, 11b, 11c, 11ld) of the front walls (7, 8) of the housing walls (4) through parallel and profiled surfaces (12), and has an ignition unit (18, 19). disposed between the sector-like depressions (9a, 9b, 9c, 9d) on one of the flat sections (11a, 11b) of the front walls (7, 8) of the housing (4), with the front faces (13a, 13b) of the rotor (1) ) together with the combustion section (Bp B _{2) of} the compression section (A? ₂₎ and expansion section (Cp _C2) sector-like form, and the sur destination region (A? ₂₎ is provided (14, 15) at least beömlésszabályzó for one blend component units, said expansion section (Cp _C2) in turn is provided with kiömlésszabályzó unit (16, 17) and the combustion zone (Bp B ₂₎ the rotor (1) being positioned downstream of the compression section (Ap A ₂ ), and the rotor (1) having uniformly distributed continuous radial grooves (20), in which the piston-like pistons (21) are disposed axially, the front surfaces cooperate with the front walls (7, 8) of the housing (4) and the sector-like sections (Ap A ₂ , Bp B ₂ , Cp C ₂ ) are separated by a variable space. ·· ·· · »· * · · · · Φ ·· ♦ ··« ·· ·· - divided into 26-toothed chambers (22), characterized in that recesses (23) are formed on the face surfaces (13a, 13b) of the rotor (1) and that the ignition unit (18, 19) is a ring. is disposed within an inner edge of the recess (23) which is closer to the center of rotation (01-01) of the rotor (1) and the outer edge of the recess (23), where the central angle (^) of the recess (23) is smaller than The central angle (T) of the flat sections (11a, 11b, 11c, 11ld) of the front walls (7, 8) of the housing (4). A rotary piston machine according to claim 1, characterized in that the rotor (1) is arranged with a gap of 0.03 to 0.3 mm from the front walls (7, 8) of the housing (4). Rotary piston machine according to claim 1 or 2, characterized in that at least part of the wall of the recess (23) is formed as a rotating surface. Rotary piston machine according to Claim 1 or 3, characterized in that it comprises a gas flow blocking unit (24) between the variable volume chambers (22), which is a cylindrical wall (6) of the housing (4) and a rotor (1). ), is connected to the rotor (1) and contacts the front walls (7, 8) of the housing (4). ··· * ·· * · · · · · · · · · · · ··· Rotary piston machine according to claim 4, characterized in that it is a gas passage. the barrier unit (24) is provided with a ring (25) which rests and is rigidly connected to the circumference of the rotor (1) and a series of grooves (27) on the rim (25) of the ring (25) facing the cylindrical wall (6) of the housing provided with a casing (26) which is concentric with the ring (25) and is fixed to the cylindrical wall of the housing (4) and which together with the grooves (27) forms a labyrinth seal. Rotary piston machine according to Claim 5, characterized in that an annular collecting channel (30) is provided on the outer surface of the ring (25), which is provided with radial channels (29) of the rotor (1) through the channel (31) formed in the ring (25). ), which are connected to the through radial grooves (20) and the axial channels (28) of the rotor (1), and these axial channels (28) are connected to a lubricant source, which passes through the collecting channel (30) through a drain channel (32). is connected.