WO2007026323A1

WO2007026323A1 - Rotary piston engine

Info

Publication number: WO2007026323A1
Application number: PCT/IB2006/053041
Authority: WO
Inventors: Wolfram Martin
Original assignee: Wolfram Martin
Priority date: 2005-09-01
Filing date: 2006-08-31
Publication date: 2007-03-08

Abstract

The invention relates to a rotary piston engine for liquid and gaseous fuels. Said rotary piston engine is substantially characterized in that a rotary piston (1) is provided with a protrusion (2) which creates a suction chamber (18), an ignition chamber (9), and a combustion chamber (10) in a cylinder housing in cooperation with a first control cylinder (6), a second control cylinder (7), and a third control cylinder (8). The inventive rotary piston engine has a small volume, runs at high speed, and is inexpensive and operationally safe to produce. The disclosed rotary piston engine can also be composed of ceramic parts and can be operated with hydrogen.

Description

Rotary engine

Technical area

The invention relates to a rotary engine. Essentially, the rotary piston engine according to the invention consists of a cylinder housing and one or more control chambers provided in the cylinder housing. Furthermore, the suction chamber, ignition chamber and internal combustion engine and a corresponding rotary piston are provided.

The invention is applicable to liquid and gaseous fuels.

State of the art

Rotary engines are also known under the name Wankel engines, which have been named after their inventor Felix Wankel. A Wankel engine is a Internal combustion engine, which consists essentially of a rotary piston which is arranged on an eccentric shaft and in a cylinder housing (also called Trochid housing) revolves and at the same time rotates about its own axis. The outer contour of the rotary piston is composed of three flattened circular arcs, which form a so-called Reulerux triangle. In each corner and side surface are appropriate sealing elements, which ensure that the suction chamber, ignition space and combustion chamber arise.

From the prior art, further rotary engines are known.

For example, DE 195 13 046 A1 discloses a rotary piston engine whose piston rotates in a circular manner and whose kinetic energy is impaired by no upper and lower door point of the piston.

For example, from FR 1 320 880 an explosion engine is known. This also has a rotating cylindrical-shaped circular piston, wherein further three control cylinders are provided which are rotatably mounted on an axis. By a turbine drive, the rotary piston is set in rotation and the corresponding control cylinder oscillate about its axis. They strike against the wall of the cylinder-shaped circular piston. The control cylinders are arranged such that the intake space, ignition space and combustion chamber form accordingly.

Furthermore, a rotary piston engine is known from US Pat. No. 5,595,151 which has a circular piston which is egg-shaped in cross section and which rotates in a circular cylinder space. Furthermore, two control cylinders are provided, which are also responsible for the corresponding division in the suction chamber, ignition chamber and combustion chamber. Object of the invention

The object of the invention is to further develop the geometry and sequence of movements of a rotary piston engine such that it can be produced cost-effectively. The goal is to provide a small, fast-running engine that is simple in design.

The object is solved by the characterizing part of claim 1.

The core idea of the solution is to form a rotary piston with a corresponding projection, which forms a suction chamber, ignition chamber and a combustion chamber in interaction with three control cylinders. The projection is a design that goes beyond the circular cross section of the rotary piston and, for example, represents a one-sided, egg-like training. It is not essential that there is a 100% seal between the circumference of the rotary piston and the cylinder housing in which the rotary piston rotates. The rotary piston is mounted on the side walls of the cylinder housing.

The cylinder housing is very simple in cross section. It is advantageously circular and has recesses in which the control cylinders also rotate on axes. The control cylinders themselves move 360 degrees and are driven via the rotary piston, for example via a transmission or the like. Due to the simple configuration, it is possible to form the rotary engine itself of ceramic. This has the advantage that a very fast-running and economically efficient rotary engine can be realized.

Another advantage of the invention is that the bearings of the control cylinder are arranged outside the actual cylinder chamber. This distance to the cylinder housing itself has the advantage that the bearings are not exposed to high temperatures, as they occur in the cylinder housing itself. As a result, for example, bearings can be equipped with conventional ball bearings, but also with ceramic ball bearings. This in turn is a cost advantage but also an advantage that can be seen in the fact that the rotary engine can be easily configured.

In an advantageous embodiment of the invention, the first control cylinder, the second control cylinder and the third control cylinder in its cross section on the geometry of a half-moon, wherein starting from a circular cross section, an outer surface portion of the respective control cylinder is convex. This offers the advantage that in a complete rotation of the respective control cylinder to the respective own axis of the space in the cylinder housing is always separated into the suction chamber, ignition chamber and combustion chamber, since the rotary piston relative to the control cylinders advantageously rolls without a gap.

In a further advantageous embodiment of the invention, the third control cylinder or its control chamber has a so-called bypass channel. This bypass channel has the advantage that the flow rate of the combustion gases is ensured at all angular positions of the rotary piston engine and the third control cylinder.

In another advantageous embodiment of the invention, the second control cylinder comprises a chamfer at one of the two transitions between the semicircle and the convex surface. This has the advantage that the fully compressed air from the suction chamber can get into the ignition space.

A further alternative embodiment provides that a further control chamber is provided in the region of an inflow opening in the cylinder housing. This control chamber also includes a control cylinder. This control cylinder is, like the other control cylinder also, connected to the rotary engine via a corresponding gear. This fourth control cylinder is assigned the task to complete the inflow opening in such a way that the combustion gases, which eventually enters the suction through the expansion within the cylinder chamber, not from the Inlet opening can escape. The fourth control cylinder thus assumes the function of an inflow valve.

Further advantageous embodiments will become apparent from the following descriptions, the drawings and the claims.

drawings

FIG. 1 a shows a plan view of a rotary piston according to the invention; FIG.

Fig. 1 b is a plan view of the rotary piston of Figure 1 a with associated sealing elements.

Fig. 2-8 is a schematic sectional view through a cylinder housing, wherein the control cylinder in different positions during a work cycle (suction, compression, working and ejection) of the rotary engine are shown.

Description of an embodiment

FIG. 1 a shows a rotary piston 1 according to the invention. The rotary piston 1 is cylindrical and has a projection 2. The rotary piston 1 rotates about its central axis 13. As already described, the rotary piston 1 according to the invention is configured cylindrical. It has a circular cross-section with a diameter D. The diameter D is smaller than the inner diameter of the cylinder space shown in FIGS. 2 to 8. Further, on the outer circumference of the cylindrical rotary piston 1 which is approximately triangular in cross-section on the projection 2 is arranged. The height of this triangular projection 2 is dimensioned such that the diameter D plus the height H the inner diameter of the cylinder space shown in FIGS. 2 to 8 result. Thus, the tip of the projection 2 slides on the inner wall of the cylinder chamber. With regard to the function of the rotary piston 1, reference is made to the description of FIGS. 2 to 8.

The rotary piston 1 has an imbalance compensation means 3 in the form of a bore. In addition, imbalance compensation means 3 may be configured in different holes or cutouts also in the region of the projection 2 and filled with material of lower density. Furthermore, unbalance compensation means 3 according to the invention can also be carried out circumferentially outside of the cylinder housing. The rotary piston 1 can be cooled, for example via an internal air cooling.

FIG. 1 b shows the rotary piston 1 according to FIG. 1 a, wherein the rotary piston 1 comprises a sealing strip 23 on the end face of the projection 2. The sealing strip 23 is guided in a groove of the projection 2. In an advantageous embodiment, the length of the sealing strip 23 is longer in comparison to the length of the rotary piston. 1 In this embodiment, the respective free ends of the sealing strip 23 are each guided in a groove, which are embedded in the inner surfaces of the top and bottom of the cylinder housing, to avoid catching the sealing strip 23 with the control chambers. Further, on the height H of the projection 2 at the top and bottom of the projection 2 each have a sealing strip 24 is arranged. For example, the sealing strips 24 are guided in a groove of the projection 2 and are pressed by means of corrugated springs to the inner surfaces of the upper and lower sides of the cylinder housing. Not shown in Figure 1 b, each a sealing ring in a circular groove, which is arranged on the inner surface of the top and bottom of the cylinder housing, fixedly mounted. The outer diameter of the sealing rings corresponds to the diameter D of the rotary piston. 1 For example, the sealing rings are pressed in each case via corrugated springs to the top and bottom of the rotary piston 1.

FIG. 2 shows a circular cylinder housing 5 of the rotary piston engine according to the invention. In the cylinder housing 5 is a first control chamber 15, a second control chamber 16 and a third control chamber 17 are arranged. The respective control chambers 15, 16, 17 are arranged such that at least the center of the respective cylinder-shaped control chambers is outside the inner diameter of the cylinder chamber. The control chambers 15, 16, 17 are configured in such a way that they connect to the inner wall of the cylinder chamber in a semicircular to three-quarter circle and are connected to it in a fluid or gaseous manner. The arrangement is such that the distance between the first control chamber 15 and the further control chamber is greater than the distance between the second control chamber 16 and the third control chamber 17th

The first control chamber 15 serves to receive a first control cylinder 6, the second control chamber 16 for receiving a second control cylinder 7 and the third control chamber 16 for receiving a third control cylinder 8. The first control cylinder 6, the second control cylinder 7 and the third control cylinder 8 have a Geometry in the form of a semicircle, wherein the diameter-forming surface of the control cylinder 6, 7, 8 arched outwards, ie convex, designed. They have a half-moon-like appearance in cross section.

In a preferred embodiment, the control cylinder 8 comprises sealing means on the surface forming the diameter in order to produce an optimum seal with the rotary piston 1 in the position shown in the following FIGS. 6 to 8.

Between the second control chamber 16 and the third control chamber 17, an ignition chamber 9 for receiving a spark plug, not shown, and / or an injection nozzle is arranged. Before and after the first control chamber 15, an outflow opening 1 1 and an inflow opening 12 is arranged in the cylinder housing 5.

After insertion of the rotary piston 1 in the cylinder chamber of the cylinder housing 5, the cylinder space by the first control cylinder 6, the second Control cylinder 7 and the third control cylinder 8, which are preferably connected via gear to the rotary piston 1, divided into three spaces: between the first control cylinder 6 and the second control cylinder 7 in a suction chamber 18, between the second control cylinder 7 and the third control cylinder 8 in an ignition space 9 and between the first control cylinder 6 and the third control cylinder 8 in a combustion chamber 10th

Immediately adjacent to the inner wall of the third control chamber 17, a bypass channel 4 is incorporated to ensure the flow rate of the combustion gases at all angular positions of the rotary piston 1.

Imbalance compensation means can be effected by one or more bores or cutouts on the first control cylinder 6, the second control cylinder 7 and the third control cylinder 8. Functional for the rotary piston 1 and the first control cylinder 6, the second control cylinder 7 and the third control cylinder 8 are also balancing weights on the axes outside the cylinder housing 5 to compensate for an imbalance in the operation of the rotary piston engine.

The projection 2 of the rotary piston 1 has a front side V and a rear side R. The front side V and the rear side R are slightly convex to the outside in order to achieve a gap-free rolling of the rotary piston 1 relative to the first control cylinder 6, the second control cylinder 7 and the third control cylinder 8. Front and back refer in the direction of rotation 19 of the rotary piston. 1 This means that the front side V of the rotary piston densifies the inflowing gas and the back side R faces the ejection side.

The rotary piston 1 rotates about its center axis 13. The first control cylinder 6, the second control cylinder 7 and the third control cylinder 8 are each a cylinder with a semicircle-like cross section. The second control cylinder 7 comprises a phase 14 which is wedge-shaped and extends over a part of the control cylinder 7. The mode of operation during a work cycle with the four strokes suction, compression, operation and ejection provided will now be described with reference to FIGS. 2 to 8.

aspiration:

In Figure 2, air or air-fuel mixture, hereinafter referred to only as air 21, sucked via the inflow opening 12 into the suction chamber 18 by rotation of the rotary piston 1 in the direction of the arrow 19.

The rotary piston 1 assumes the position that the tip of the projection 2 of the rotary piston 1 has immediately passed the outflow opening 1 1. The tip of the projection 2 comes into direct contact with the first control cylinder 6, which is arranged in the control chamber 15. The remaining control cylinders 7, 8 roll on the peripheral surface of the rotary piston 1 in its circular cross-section area.

Sealing:

In FIG. 3, the sucked-in air 21 in the suction space 18 is compressed by the front side V of the projection 2. The tip of the projection 2 of the rotary piston 1 has now passed the inlet opening 12 and thus seals the suction chamber 18 from. The suction chamber 18 is bounded on one side by the cylindrical outer wall of the rotary piston 1 and the cylindrical inner wall of the cylinder chamber, wherein the lateral boundary is done by the projection 2 just described and by the corresponding position of the second control cylinder 7. By further rotation of the rotary piston 1 in the direction of arrow 19, the trapped air 21 continues to compress until the compressed air 21 passes from the suction chamber 18 into the ignition chamber 9 via a gap formed by the phase 14 of the second control cylinder 7 and the rotary piston 1 (Fig. 4). The gap between the second control cylinder 7 and the rotary piston 1 forms exclusively in this position shown and is for a Overflow of the compressed air 21 from the suction chamber 18 into the ignition space 9 is required.

In Figure 5, the gap between the second control cylinder 7 and the rotary piston 1 is closed again. The air 21 is further compressed in the ignition space 9. The tip of the projection 2 contacts the crescent-shaped side of the circular control cylinder 7, which is circular in nature, thus closing the ignition chamber 9 on one side. On the other side of the third control cylinder 8 is provided for completing the ignition chamber 9, the circular cylinder jacket surface slides on the lateral surface of the rotary piston 1. By a further rotation of the rotary piston 1 in the direction of arrow 19, the air 21 is compressed so far until the position shown in FIG. 6a is reached.

Work:

In FIG. 6a, the compression of the air 21 is greatest. Ignition is triggered via a spark plug or fuel injection. The resulting expansion of the combustion gases already acts after 5 degrees rotation in the direction of the arrow 22 on the back R of the projection 2 and thus moves the rotary piston 1 in the direction of arrow 19. The position shown in FIG. 6a is chosen such that by the explosive acting pressure within the ignition chamber 9 a large attack surface is provided both on the control cylinder 7 and on the other control cylinder 8 and on the rotary piston 1 itself. Therefore, the position is assumed, as shown in Fig. 6a, in which the tip of the projection 2 has already exceeded the center of the ignition chamber 9, so that the resulting pressure on the back R affects the area. The rotation of the control cylinder 7 and 8 is supported accordingly.

FIG. 6b shows an alternative embodiment to FIG. 6a. In Figure 6b, the cylinder housing 5 comprises in the region of the inflow opening 12, a fourth control chamber 25 for receiving a fourth control cylinder 26. The fourth control cylinder 26 is also like the first 6, second 7 and third control cylinder 8 connected to the rotary piston 1 preferably via gears. In the position of the fourth control cylinder 26 shown in FIG. 6, the latter closes off the inflow opening 12 in such a way that the combustion gases which could possibly enter the intake space 18 through the expansion can not escape from the inflow opening 12. The fourth control cylinder 26 thus assumes the function of an inflow valve.

In Figure 7, the expansion of the combustion gases acts on the back R of the projection 2 and also on the adjacent surface of the third control cylinder 8. The area on the rotary piston 1 is always larger by the rotation in the direction of arrow 19, so that the pressure increases in terms of area and the Rotation thus supported.

In FIG. 8, the tip 20 of the third control cylinder 8 facing the ignition space 9 opens an access for the combustion gases, so that they additionally act on the rear side R of the projection 2 in the direction of the arrow 22 via a bridging channel 4. The combustion gases pass through the bridging channel 4 from the ignition chamber 9 into the combustion chamber 10. As a result, despite the opening of the ignition chamber 9, the rotation of the rotary piston 1 is supported.

ejection:

In Figure 2, the outflow opening 1 1 is released by the movement of the rotary piston 1 in the direction of the arrow 19 through the projection 2, so that the combustion gases are expelled from the combustion chamber 10.

Depending on the design of the rotary piston engine, the air 21 described in FIGS. 2 to 8 forms the fuel mixture, provided that no fuel injection into the ignition space 9 takes place.

Variants of slight angular changes of the vertex to the fulcrum of the rotary piston 1 of the first control chamber 15, the second control chamber 16th and the third control chamber 17 to each other are also functional. For example, an angular magnification of the first control chamber 15 and the third control chamber 17 results in an increase in volume of the combustion chamber 10 and a reduction in volume of the suction chamber 18. This angular magnification appears useful in a charged rotary engine, for example, if the first control chamber 15 and the third control chamber 17 in an imaginary straight Line are arranged through the central axis 13 of the rotary piston 1 directly opposite, since in this variant, the combustion pressure an increased time unit acts on the rotary piston 1 and thus the efficiency increases.

The axial width of the cylinder housing 5, the rotary piston 1 and the first control cylinder 6, the second control cylinder 7 and the third control cylinder 8 results from the material strength of the first control cylinder 6, the second control cylinder 7 and the third control cylinder 8, which are exposed to considerable pressures ,

In one embodiment of the invention, the material of the rotary piston engine is ceramic and hydrogen is the fuel. By choosing the material ceramic and the achievable higher rotational speeds of the rotary piston compared to the metal material, the sealants are not required.

Claims

1 . A rotary piston engine, essentially comprising a cylinder housing (5), a rotary piston (1) which is mounted in the cylinder housing (5), a suction chamber (18), an ignition chamber (9), combustion chamber (10), an inflow opening (12), an outflow opening (1 1), characterized in that the rotary piston (1) is cylindrical, whose central axis (13) on the

Center of the cylinder housing (5), and the rotary piston (1) has a

Projection (2), the suction chamber (18) through the rotary piston (1) and a first

Control cylinder (6) and a second control cylinder (7) of the

Ignition chamber (9) and the combustion chamber (10) is separated, the ignition space (9) through the rotary piston (1) and the second

Control cylinder (7) and a third control cylinder (8) of the

Suction chamber (18) and the combustion chamber (10) is separated, the combustion chamber (10) through the first control cylinder (6) and the third control cylinder (8) of the suction chamber (18) and the

Ignition chamber (9) is disconnected, the cylinder housing (5) a first control chamber (15), a second

Control chamber (16) and a third control chamber (17) comprises wherein the first control chamber (15) for receiving the first control cylinder (6), the second control chamber (16) for receiving the second control cylinder (7) and the third control chamber (17) for receiving the third control cylinder (8).

2. Rotary piston engine according to claim 1, characterized in that the rotary piston (1) in its diameter (D) is designed such that the cylindrical part of the rotary piston (1) in its diameter (D) is formed smaller than the cylinder space of the rotary piston ( 1) and the rotary piston (1) together with the projection (2) corresponds almost to the diameter (D) of the cylinder chamber.

3. Rotary piston engine according to claim 1, characterized in that the first control cylinder (6), the second control cylinder (7) and the third control cylinder (8) has a semicircular geometry in cross section through its own axis, wherein the diameter-forming surface is convex is.

4. Rotary piston engine according to claim 1, characterized in that the third control chamber (17) comprises a bridging channel (4).

5. A rotary engine according to claim 3, characterized in that the second control cylinder (7) comprises a phase (14) at one of the two transitions between the semicircle and the convex surface.