DE3321270A1 - Rotary engine - Google Patents

Abstract

Known rotary engines are of complex construction and have an unfavourable torque characteristic. Rotary engines are therefore proposed with rotationally symmetrical rotary pistons arranged concentrically with their axis of rotation, both the internal chamber of the housing and the rotary piston being respectively equipped with sealing areas for dividing the housing internal chamber into an inlet and compression area on the one hand and an expansion and exhaust area on the other, it being possible to arrange these areas in series in a multiple series circumferential direction. The compressed medium is at the same time fed to the combustion chamber by way of a precombustion chamber.

Description

PATENT ADVERTISER MANFRED "lJERMÄNKI ..:.

EUROPEAN PATENT ATTORNEY

APPROVED REPRESENTATIVE AT THE EUROPEAN PATENT OFFICE

Düren - Josef-Schregel-Straße 19 -χ

Patent attorney M. Liermann, Josef-Schregel-Str. 19, D-5160 Düren

Registered mail

To the

German Patent Office

Zweibrückenstrasse 12

8000 Munich 2

Telephone (0 24 21) 174 telegrams: Lierpatent Düren

Postal check Cologne 305 715-500 (BLZ 370 100 50)

Deutsche Bank AG Diiren 811 0959 (BLZ 395 700 61)

Deutsche Bank AQ Erkelenz 774 040C (BLZ 310 70001)

your signs

Your message

My characters (164) / In Düren
• 10. June 1983

Patent application

claiming the internal priority from G 83 09 593.4 of March 31, 1983

Applicant:

Heinz Schneider Kaisersruhestrasse 5102 Würselen

Title:

Rotary piston engine

Rotary piston motor

The invention relates to a rotary piston engine with an ignition device, at least one concentric to one Housing arranged on the axis of rotation with inlet and outlet channels and at least one rotary piston which is arranged concentrically to the axis of rotation and which has rotating sealing areas for sealing having against the inner wall of the housing. Here, the rotating sealing areas can also be radial acting movable sealing elements be formed.

Rotary piston engines of the type described at the outset have become known, for example, from Austrian patent specification No. 247071. However, the structure of this engine is relatively complicated. It becomes difficult to remove the torque from the rotary piston. In the engine mentioned, the compression chamber is also limited by two lamellae, so that after ignition has taken place, only the difference area between the two lamellae can be used as an area for applying the explosion pressure and thus for generating the torque. If the ignition takes place at the time of the greatest compression, there is no differential pressure area at all, so that the engine must first be turned beyond this dead center in order to Ignition to be effective at all. However, because of the slowly increasing differential area, this means an only slowly increasing torque. This increase in torque is further slowed down by the fact that, with increasing angle of rotation, the combustion pressure also decreases because of the larger combustion chamber.

In contrast, the invention is based on the object

to propose a rotary piston engine that is simple in construction

and is safe to operate and shows better torque behavior.

"a"

In the case of a rotary piston engine, this task is the one at the beginning described type solved in that the housing in the UmIaufrichtung stationary sealing areas for demarcation of rooms of different functions and that at least one antechamber and openings for transferring of the compressed medium are provided in the combustion chamber. The rotary piston is fixed against rotation with the axis of rotation tied together. The construction described represents a very simple construction because the rotary piston is now direct sits on the axis of rotation and can also be arranged there, so that the torque is therefore direct and simple can be removed. The stationary sealing areas, which are in addition to the sealing areas of the rotary piston are provided, ensure that the explosion pressure no longer has to work against a differential area of two limiting units on the rotary piston itself, but that the full area on the rotary piston is available to him, while the reaction force is absorbed by the housing will. This means that there is the greatest possible immediately after ignition Torque on. This has been achieved simply by separating the suction and compression space on the one hand and expansion and expansion space on the other hand by means of the described sealing arrangement. This separation is possible because it is compressed in the compression space Medium is passed through additional channels ih the expansion space. Is now additionally taken care of that compressed medium cannot flow back in the channels at any time, so the combustion can if necessary already used in these channels.

According to an alternative solution to that of the invention lying task is particularly for those rotary piston engines in which the rotary piston acts at least radially and having movable sealing elements, it is proposed that the sealing elements in the rotary piston on four in the circumferential direction evenly distributed sealing areas are provided, with the rotary piston between the sealing areas

" _U -y W It tf" »MV A

suffice each a radially outwardly open combustion chamber with combustion channels emerging approximately at the sealing areas is provided and wherein the housing in the circumferential direction in four each the distance between two adjacent Sealing areas comprehensive zones is divided, of which a first zone between the inlet and outlet channel and one of these diametrically opposite second zone sealingly abuts the circumference of the rotary piston, while one third and a fourth zone diametrically opposite this forms a radial distance from the rotary piston, wherein the third zone in the direction of rotation at the beginning with the inlet channel and the fourth zone in the direction of rotation at the end is connected to the outlet channel and wherein the ignition device is provided in the region of the second zone. Even With such a construction, that of invention becomes underlying task completely solved. Pre-chambers can be avoided with this construction.

In one embodiment of the invention according to the first alternative it is provided that the antechamber as Connection is formed, which the combustion chamber with the means for delivery of the compressed Medium connects. This simplifies the construction work »because in many cases the simple connection line is already available ala antechamber is sufficiently large.

Another embodiment in turn provides that the Antechamber in the correspondingly hollow rotary piston is provided, the antechamber via a slot control with the combustion chamber on the one hand and with a Compression space on the other hand is connected. This makes a sufficiently large one even with larger motors Pre-chamber provided, at the same time by the arrangement of the pre-chamber in the rotary piston of the rotary piston is cooled by the inflowing and still cool medium. This measure also creates an additional, old »Pre-chamber acting component avoided.

Another embodiment of the invention in turn provides that the sealing areas on the one hand as radially movable Sealing elements and on the other hand as cam-shaped sealing areas are formed with a sealing zone. With this design, it is easily possible that the stationary and the circumferential sealing areas do not hinder one another, but can slide over one another without further ado.

A supplementary embodiment of the invention provides that the radially movable sealing elements are arranged in the rotary piston and the cam-shaped sealing areas in the housing are. As a result, the rotary lobes from vane pump construction are used already - known construction can be used and the construction of the housing will also be problem-free manageable.

Again, an alternative embodiment of the invention provides that the radially movable sealing elements in Housing and the cam-shaped sealing areas on the rotary piston are trained. This reversal is particularly beneficial if the engine is already supplying compressed medium will.

Another embodiment of the invention in turn provides that each diametrically opposed at least two radially movable sealing elements and at least two cam-shaped sealing areas are arranged, two such Devices act non-rotatably on the same axis of rotation and one as a compressor and the other as a motor is working. This makes it very easy to identify the hot area and the cold area of the entire machine kept mechanically separated from each other. In addition, a simplified engine construction is enabled because the motor is already being supplied with compressed medium.

Yet another embodiment of the invention provides before that the housing closely adjacent in the circumferential direction and has inlet and outlet openings arranged in pairs, which via a sealing element sealing on the rotary piston are separated from each other. In this way, the respective chamber volume can be maximized or the desired size be minimized.

Furthermore, it is provided according to one embodiment of the invention, that the rotary piston over three evenly distributed arranged sealing elements against the inner wall of the housing seals and that in the direction of the suction opening an inlet area, a stationary sealing area, an outlet area, an outlet opening and a stationary one Sealing area follows- This arrangement enables problem-free Combination of the hot area and cold area of the engine and creates with the smallest structural effort a reliable and powerful unit.

Yet another embodiment of the invention provides that the rotary piston has six sealing elements in the arrangement described and that the areas of the housing described above in the direction of rotation in
repeat the sequence described once. In such an arrangement, the double ignition sequence and thus a corresponding increase in torque is possible with only insignificantly increased construction costs. This arrangement also enables the ignition zones to be arranged diametrically opposite one another so that the explosive forces on both sides of the rotary piston cancel each other out (this also applies to the compression forces) and thus the rotary piston is freed from unpleasant radial loads.

No further supplementary embodiment of the invention sees before that the number of sealing elements of the rotary piston is multiplied, the above-described areas

m "» » if m wt * A

of the housing in the sequence described as well are multiplied by the factor of multiplication. Through this it becomes possible to accommodate an almost unlimited number of explosion sequences in one engine. The rotary piston can be designed with a large diameter, so that a large scope is available for distribution stands. At the same time, the large diameter of the rotary piston results in a particularly favorable torque behavior reached and it can alternatively even lower the combustion pressure and thus reduce the load on the sealing areas will. This eases the problem of sealing.

Another embodiment of the invention provides that Inlet and outlet channels are provided on the end faces of the housing. This allows access to the compression and expansion spaces simplified.

Yet another embodiment of the invention provides before that the successive in the circumferential direction Spaces are separated from each other by sealing areas of the housing. This results in a particularly simple structure of the entire facility.

Another embodiment of the invention provides that the inner wall of the housing has a circular cylindrical cross section and is radially movable in the housing Sealing elements against the circumferential surface of the Rotary piston is sealed, whereby the rotary piston in the circumferential direction cam-shaped sealing areas for sealing having against the circular cylindrical inner wall of the housing. The circular cylindrical design of the housing is special easy to manufacture. The different spaces are formed here by the shape of the rotary piston, which is due to the even distribution of these spaces is exactly massive

can circulate and is also easy to edit.

It is also provided according to one embodiment of the invention that the cam-shaped sealing elements have at least radially directed openings as a sealing zone to supply at least the gap between Inner wall of the housing and the closest opposing surface of the rotary piston with compressed medium. Through this a non-contact seal of sufficient quality can be achieved.

Another embodiment of the invention provides a rotary piston engine with an ignition device, at least a housing arranged concentrically to an axis of rotation with at least one inlet and outlet channel and at least one Rotary piston arranged concentrically to the axis of rotation with radially extending sealing areas for sealing against the inside wall of the housing that the sealing areas are tooth-shaped with flanks that can be rolled off, each tooth-shaped sealing area with a corresponding tooth gap of rotatably mounted sealing rollers to subdivide the interior of the housing into inlet and compression areas as well as expansion and outlet areas cooperates. In this way, radially movable sealing elements can be avoided. So are also avoided the friction of these sealing elements on the circumference of the rotary piston on the one hand and the friction the sealing elements in their guides during their radial movement. The sealing rollers used instead are in their structural design and in their drive easily manageable and easy to manufacture, with the sealing rollers with relatively high pressure on the corresponding circumferential surface of the rotary piston can be pressed to produce the necessary tightness. This results in only a minor one Loss, because both bodies roll off one another. If then during the rotational movement of the rotary piston the sealing tooth of the rotary piston, which seals against the inner wall of the housing at its end face, into the area

the sealing roller comes, then he enters there in a correspondingly provided tooth gap. Tooth gap and sealing tooth can for example be designed in the form of an involute toothing, so that the tooth flanks of tooth gaps and tooth perform as extensive a rolling movement as possible on each other, so here too, if possible Sliding friction with all its disadvantages can be avoided.

According to a supplementary embodiment of the invention it is provided that the sealing rollers have a constant translation are driven to the rotary piston, the translation is designed so that each one incoming tooth with an incoming tooth gap can work together. One such coupling of the rotary piston with the sealing rollers, for example via meshing spur gears, ensures that the sealing tooth is always on a corresponding one, even with unusual engine loads Tooth gap abuts, so that a destruction by phase shift of the two belonging to one another Parts is avoided. The construction costs to be carried out for this are no greater than the construction costs for conventional ones Motors for driving the camshaft to control the valves.

Another embodiment of the invention provides that each prechamber has a check valve because of backflow is locked in the compression room. This can on the one hand undesired losses and on the other hand unwanted vibrations of the gas column can be avoided.

Finally, according to one embodiment of the invention, it is also provided that 'each combustion chamber BEZW. the Expansion and outlet area via a check valve is blocked against backflow into the antechamber. It gives this an additional backup that is independent from the wear or sealing condition, possibly slot controls a flashback of the explosion flame into the Pre-chamber prevented.

üie invention will now be based on the accompanying drawings, show the exemplary embodiments are described in more detail. Show it:

Figure 1 section through a motor perpendicular to the axis of rotation

FIG. 2 view in the direction of arrow A according to FIG. 1

Figure 3 side view of a device with separately arranged motor and compressor

Figure 4 Section A-A according to Figure 3 Figure 5 Section B-B according to Figure 3

Figure 6 side view of a device with separated arranged motor and compressor

FIG. 7 section CC according to FIG. 6 FIG. 8 section DD according to FIG. 6

Figure 9 side view of an engine with vertical standing axis of rotation

FIG. 10 section E-E according to FIG. 9

FIG. 11 a quarter section showing a breakout in view according to arrow F according to figure

Figure 12 cross section through a construction variant

Figure 13 cross section through a construction variant FIG. 14 partial section G-G according to FIG. 15 partial section H-H according to FIG.

FIG. 16 rotary piston engine in a section like FIG. 13, but with sealing rollers as a seal

3 ^ 2 Ί ^ 7 U

The design of a motor according to FIG. 1 represents an alternative solution to the object on which the invention is based. A rotary piston 60 with a circular cylindrical cross-section is arranged on a rotary shaft 10 in a rotationally fixed manner. The rotary piston 60 has sealing areas 56, 57, 58 and 59 that are uniformly distributed in the circumferential direction and are designed as slots. Radially movable sealing elements 52 to 55 are arranged in the sealing areas mentioned. Said sealing elements can in turn consist of elements which can be individually displaced relative to one another and which can also be spread in the axial direction, as shown in FIG. The construction mentioned is used for better sealing. The sealing elements mentioned can be under a preload generated in a suitable manner, for example by a compressed medium, when the rotating piston 60 is rotating slowly, as a result of which the sealing elements mentioned are pressed radially outward. At high speed, the centrifugal force that occurs is sufficient for this.

A combustion chamber 68, which is open radially outward, is arranged between each of the sealing areas 56 to 59 is, with two combustion channels 72 to 79 opening into each of these combustion chambers, each of which has its outputs in the immediate vicinity Close to an assigned sealing area 56 to 59 lie.

The rotary piston 60 is surrounded by a housing 16 which has an approximately tangentially directed inlet channel 24 and also an approximately tangential outlet channel 43 has. The inner distance between both channels in the circumferential direction of the rotary piston 60 is c? about as large as the distance between two adjacent rotary piston », in the exemplary embodiment in the rotational position shown between the sealing areas 56 and 59. In this area, the housing 16 also has the smallest possible Gap to the rotary piston 60.

\ J \ J IL. , t- r

VZr--

A zone of the same is located diametrically opposite the mentioned area between inlet channel 24 and outlet channel 43 Circumferential dimension provided in the housing 16, which is also rests as closely as possible on the rotary piston 60, that is, as sealingly as possible. About in the middle of this area is one Ignition device 1 is provided, which can be equipped with a conventional spark plug.

To the two closely-fitting areas described Rotated by 90 °, the housing 16 has an inlet area 36 and diametrically opposite one another on the one hand on the other hand an outlet area 51. These areas of the housing 16 have a variable distance to Circumferential surface of the rotary piston 60, so that between the inner wall of the housing and the circumferential surface of the rotary piston arise in cross-section sickle-shaped chambers.

The motor in the embodiment of Figure 1 operates as follows. When describing how it works, a rotational position as shown in FIG. 1 can be assumed.

If the motor is rotated further in the direction of arrow 155, starting from the aforementioned rotational position, this occurs Sealing element 52, since it remains in contact with the inner circumferential surface of the housing 16, in the inlet area 36 a, so that as a result, for example, a fuel-air mixture is sucked in through the inlet channel 24. If such a rotation of 90 ° has been carried out, then this is the Inlet area 36 is filled with a fuel-air mixture and is then enclosed by the sealing elements 52 and 53. If you turn it again, the sealing area will now 52, the inlet area 36 narrows, so that the fuel-air mixture present in this area is in the Combustion chamber 71 collects and is compressed there. With the highest compression a situation is reached, as sio enclosed by the density elements 53 and 54

will. The combustion chamber 71, which has then become the combustion chamber 68, is located below the ignition device 1 and ignition can now take place. Insofar as the explosion pressure that occurs after ignition escapes into combustion channel 73, no incorrect force can be exerted on rotary piston 60 as a result, because there is no corresponding contact surface. The sealing element 53 has completely disappeared radially in the rotary cap 60. The same applies initially to the part of the explosion pressure that propagates into the combustion channel 72 . However, with the slightest further rotation of the rotary piston 60, a corresponding contact surface on the sealing element 54 arises immediately, which increases very quickly as the sealing element 54 migrates into the outlet area 51 during the further rotation of the rotary piston 60. A further rotation by 90 ° then results a situation as it is enclosed by the sealing elements 54 and 55. The explosion pressure is now completely relaxed and the outlet channel 43 has just been opened by the sealing element 55. With a further rotation of 90 °, the burned fuel-air mixture is pushed out completely by the sealing element 54 into the outlet channel 43. Residual stocks are driven out through the combustion channel directed in the opposite direction to the direction of rotation, that is, according to FIG. Another 90 ° turn makes the last described area the aspirating area again.

From the structure of the device it can be seen that an ignition can take place every time after a 90 ° rotation. at a single turn of the rotary piston are therefore

four ignitions achieved. At the same time, a kickback of the motor is reliably prevented and always will

achieves that the reaction force from the explosion pressure is always completely absorbed by the housing. One An equilibrium situation that could stop the rotary piston after ignition has taken place is not possible. This is special important for starting the motor.

A similar motor is shown in FIGS. 9 to 11. On an axis of rotation 13 is a rotary piston 63 of circular cylindrical Cross-section arranged non-rotatably. The rotary piston 63 has three evenly distributed in the circumferential direction radially movable sealing elements 122, 123 and 124. The rotary piston 63 is surrounded by a housing in it Sidewalls, the radially movable sealing elements 122, 123 and 124 are guided, for example, via a link 156 are. The housing 19 forms two different chambers around the rotary piston 63, namely the inlet region 39 and the outlet area 48. The two chambers mentioned are on the one hand wide by one in the circumferential direction extending stationary sealing area 89 and a further stationary one extending only very briefly in the circumferential direction Sealing area 88 sealed against one another on rotary piston 63 and thus separated from one another. Direct 1 inks and to the right of the stationary sealing area 88 is connected to the outlet area 48 on the one hand Outlet opening 151 and on the other hand connected to the inlet area 39 a suction opening 29 · provided. Farther In the exemplary embodiment, connecting lines acting as antechambers 101 and 102 are provided on the outside, which represent the end of the inlet area 39 with the beginning of the Connect outlet area 48 to one another. This opens up the beginning 158 of each prechamber 101 and 102, each from the end face of the engine, directly into the inlet area 39. The end 159 of the two antechambers 101 and 102 lies in the area of the beginning of the outlet area 48, opens however, in each case at the front so that the end mentioned

M β M *

159 is covered by the body of the rotary piston 63 and thus blocked.

Arranged behind the radially movable sealing elements 122, 123 and I-A in the direction of rotation of the arrow 157, overflow openings 29 are provided on both end faces of the rotary piston 63.

If the rotary piston now rotates in the direction of arrow 157, so it can be seen that, for example, the radially movable sealing element 124 from the stationary sealing area 88 Rotates coming into the position shown in Figure 10. This allows a fuel-air mixture according to known physical laws through the suction opening 29 * in the inlet area 39 are sucked into it.

However, the sealing element, which can move radially, also has beforehand 122 provided for a suction, so that between the sealing elements 122 and 124 a fuel-air mixture was included in the inlet area 39. While the rotary piston 63 continues to rotate in the direction of arrow 157 here, the radial sealing element 122 has migrated into the stationary sealing area 89, so that the radial movable sealing elements 122 and 124 enclosed chamber became smaller and smaller with progressive rotation. This caused the sucked-in fuel-air mixture compressed and pressed into the connecting lines acting as antechambers 101 and 102. An outflow these lines is not possible because the rotary piston 63 itself closed the ends 159 of these antechambers holds. Only in the course of a further rotation when the radially movable sealing element 122 enters the outlet area 48 enters, the end 159 is covered by the overflow opening 29 designed as a bevel and thus Approved. The medium, which is highly compressed within the antechambers 101 and 102, can now enter the beginning of the outlet area 48 enter. The compressed

\ J \ J C ι t - ι

Medium to be filled space is limited by the radially movable sealing element 122 and thereby a combustion chamber 107 formed. The compressed air flows into this combustion chamber 107 via the overflow opening 29, as described Medium one. As soon as the radially movable sealing element 122 has passed the area of the ignition device 6, the entire area of the overflow opening 29 is below the Exit end 159 migrated away so that the exit end 159 is closed again by the rotary piston 63. Ignition can take place at this point in time. A setback of the Flame in the combustion chamber 107 in the antechambers 101 or 102 is reliably prevented because the rotary piston is 63 closes the corresponding openings 159.

The explosion pressure generated after ignition is supported on the one hand on the housing 19 and on the other hand on the now full surface of the radially movable sealing element 122 and thus causes the desired rotary movement in Direction of arrow 157.

From the previous ignition process there are now on the other side of the radially movable sealing element 122 burned and expanded gases, which are released by the radially movable sealing elements 122 and 123 in the in FIG 10 shown position of the rotary piston 63 are included. Turn the rotary lobe a little further 63 in the direction of arrow 157 beyond the position shown in Figure 10 ensures that then the radial movable sealing element 123 opens the outlet opening 151 so that the burnt gases can flow out and in the train the further rotation of the radially movable sealing element 122 are pushed out. But it is quite conceivable although not functionally necessary, the beginning of the outlet opening 151 is already in the area of the boundary line IbO, which is indicated by dashed lines, to place,

όόΔ Ι Z / U

so that the necessary outlet cross-section is already open in the area of this boundary line 160. Through this can be prevented that due to the decreasing area of the radially movable sealing element in this area 123 an undesirable reaction of the remaining expansion pressure on the radially movable sealing element 122 occurs, which would, of course, reduce the torque.

The design of the motor described enables three ignitions during one revolution with the simplest design and avoids all unbalanced rotating masses. The greatest possible torque is available immediately after ignition available, with the reaction force always and completely supported on the motor housing. An equilibrium situation that would disrupt the running of the engine equal areas of the radially movable sealing elements cannot arise.

Figure 12 shows a motor whose principle of operation is identical to the motor according to Figures 9 to 11, the Function sequence is doubled in the circumferential direction. In the motor according to FIG. 12, a rotary piston 62 is non-rotatably arranged on an axis of rotation 14 and extends in the circumferential direction has six radially movable sealing elements 125 to 130 distributed uniformly. The rotary piston designed in this way 62 is arranged in a housing 20 which is narrow in the circumferential direction and in the direction of rotation of the arrow 161 has stationary sealing area 90, which is followed by a suction opening 30 ', an inlet area 41, a wider stationary sealing area 91, an outlet area 49 and an outlet port 153. The one described The sequence now repeats itself once more with the itself the narrower stationary sealing area adjoining the outlet opening 153 in the direction of rotation of the arrow 161 92, the inlet area 40, the wider stationary sealing

area 93, the outlet area 50 and the outlet opening 152, which is then again the narrower stationary sealing area 90 follows. In the arrangement according to FIG. 12, there is also in each case between the inlet area 41 and the outlet area

49 or between the inlet area 40 and the outlet area

50 a connection designed as an antechamber 103 or 104 provided, the outlet opening of which is closed to the outlet region 49 or 50 by the rotary piston 62 and is shown in FIG Rotational position shortly beforehand of the overflow openings 30 and 31, respectively, which was already described in relation to FIGS. 9 to 11 Way are arranged on the rotary piston 62, has been opened.

In the rotary position shown in FIG. 12, there is a compressed fuel-air mixture in the combustion chambers 108 and 109 and ignition can now take place via the ignition devices 7 and 8. The rest of the workflow is as already described for FIGS. 9 to 11. The engine of Figure 12, however, has the advantage that an even greater number of ignitions can take place during one revolution, whereby the torque behavior and the smoothness of the engine is improved or the working pressure can be lowered if necessary, whereby the Sealing problems are easier to deal with. Due to the arrangement described, the combustion chambers 108 and 109 are exactly diametrically opposite, so that the bending moment, which results from the combustion pressure and acts on the rotary piston 62, cancel each other out. The rotary piston 62 is thus free of radial loads, so that the axis of rotation 14 only has to transmit torque. At the same time, of course, this balanced arrangement ensures that the engine runs exceptionally smoothly.

Figure IP thus shows a motor according to Figures 9 to 11 its functional units on the circumference of the housing only

have been doubled, adding the added benefit of radial relief was achieved. Such an arrangement is not limited to a doubling, but rather can in principle be repeated any number of times in a row will. This makes it possible, for example possible to make a rotary piston with a very large diameter, which makes it possible to use a to build downright low-speed runners with high torque. With a multiplication in the described Art can run uninterrupted firing orders in turn, which the fluctuation of the torque can be minimized. This makes it possible to design an internal combustion engine, which runs exceptionally smoothly despite slow speed and high torque and does not require any flywheels to compensate for torque fluctuations. Ks can even succeed in designing the housing and rotary lobes in development -so in principle an engine with an infinite rotary piston diameter to build so that the HolaLion motor can even be turned into a linear motor.

In Figures 6 to 8 is a motor according to the invention shown in a modified design. In the embodiment according to FIGS. 6 to 8, the motor part and the compressor part separated from each other. Figure 6 shows the corresponding side view, in which a compressor 139 together with a motor 141 acts on the same axis of rotation 12, but with the respective housings 18 and 23 separated from one another are.

The engine part is shown as a cross section in FIG 7. On the axis of rotation 12, a rotary piston 64 is non-rotatably arranged, which is diametrically opposite Has sides radially movable sealing elements 118 and 119. The rotary piston 64 with the aforementioned radially movable Sealing elements is arranged in a housing 18, which at two diametrically opposite points inside each has a stationary sealing area 86 and 87 which seals against the rotary piston 64. This will be

two chambers to be designated as outlet areas 46 and 47 separated from one another in the interior of the housing 18.

In the rotational position shown in Figure 7, the closes stationary sealing area 86 with the radial. movable sealing element 119 a combustion chamber 105. on the side facing the violin closes the stationary sealing area 87 together with the radially movable sealing element 118 a combustion chamber 106. Both combustion chambers are equipped with an ignition device 4 or b. On the other side of the respective stationary sealing area 86 or 87, facing away from the combustion chamber 105 or 106, the housing 18 has an outlet opening 147 or 148 on.

Around the combustion chamber 105 or 106 with a fuel-air mixture To be supplied, one is to be used as an antechamber on at least one end face of the engine for each of the combustion chambers mentioned 99 or 100 formed connecting line provided, their entrance opening in the one already described Way is closed by the rotary piston 64. The rotary piston 64 has the arrangement already described Overflow openings 27 and 28, which open the antechambers 99 and 100 and are shown in FIG ürehlage have just closed again. Ignition can now take place via ignition devices 4 and 5, whereby the rotary piston 64 is rotated in the direction of the arrow 362 due to the resulting explosion pressure. The ones from the previous work cycle on the other side of the radially movable density learn te 118 and 119 in the Exhaust areas 46 and 47 still existing burned Gases were released through the outlet openings by this rotation 147 and 148 pushed out completely. Then then pass the named radially movable sealing elements stationary sealing area 86 and 87, respectively, then form the other side is the combustion chamber 105 or

OO L I Z- / U

106, which via the overflow openings 27 and 28 with compressed Medium is filled. Also with this motor construction described, the rotary piston 64 is free from bending loads, because the rotary piston 64 is always only symmetrical radially is charged.

Another housing 23, which is constructed very similarly to the housing 18 already described, is arranged on the same axis of rotation 12 and contains a rotary piston 65, which is non-rotatably connected to the axis of rotation 12, and radially movable sealing elements 120 and 121 in a diametrically opposite arrangement having.
This is the compressor 139. The compressor 139 is driven to rotate in the direction of the arrow 162 by the drive power of the motor 141. As a result, the radially movable sealing element 121 and 10 has moved into the rotational position shown in FIG. 8 and has sucked in a fuel / air mixture via the suction openings 28 'and 27, so that the inlet area 38 and 38 in the arrangement shown in FIG is filled with a fresh fuel-air mixture. If the rotation is now continued, the radially movable sealing element 122 and 121 migrates over the respective stationary sealing area 8b or 84 in front of it and further over the suction openings 28 'and 27 *, so that then each closed inlet areas 38 and 38 " which are closed on the one hand by the radially movable sealing elements and on the other hand by the stationary sealing areas. A further rotary movement ensures compression and thus forcing the fuel-air mixture through the outlet openings 149 and IbO into the antechambers 99 and 100, respectively they are fed to the motor 141 in the manner already described.
The result is an extremely simple engine structure in which the hot part and the cold part are separated from one another.

A very similar structure, in which the hot part and the hot part are also separated from one another, is shown in FIGS. 3 to b. Here too, motor 142 and compressor 140 are accommodated in separate housings 17 and 22, respectively. Both housings are arranged coaxially to the same axis of rotation 11. In the exemplary embodiment according to Figures 3 to 5, the interior of the housing 17 and 22 has a circular cylindrical cross-section, in which radially movable sealing elements 114 and 115 or 116 and 117 protrude in a diametrically opposite arrangement, which in the stationary sealing areas 83 and 82 or 80 and 81 are arranged so as to be radially movable in the above-mentioned manner and bear against the inside of the rotary piston 66 and 67, respectively, and provide a seal. The rotary piston 66 or 67 has cams 133 and 134 or 135 and 136 in a diametrically opposite arrangement. These cams seal against the circular cylindrical
Inner wall of the housing 17 or 22 from. They are of such a shape that the radially movable sealing elements can move over them.

The motor 142 has on one side of the radially movable sealing element 114 an ignition device 3 and an outlet opening 143 on the opposite side. The radially movable sealing element 115 has an ignition device 2 on one side and an ignition device 2 on the opposite side Side an outlet port 144. The motor part and the compressor part are connected to the pre-chamber 97 or 98 effective connecting line connected to each other, whereby the entry of the aforementioned antechambers into the engine part again takes place at the front and from the rotary piston 66 is locked in the manner already described. Overflow openings 25 and 26 ensure that the antechambers 97 and 98 open to the combustion chamber, depending on the angle of rotation Ul or 112.

In the rotational position shown in Figure 4, the combustion

'3'3212' / rev

tion rooms 111 and 112 freshly charged and the antechambers 97 and 98 closed again. The ignition can now take place via the ignition devices 2 and 3, r, o that driven by the explosion pressure, the rotary piston 60 rotates in the direction of the arrow 163. The residual gases still present in the outlet areas 44 and 4b from the previous work cycle are thereby completely expelled by the cams 33 and 134 through the outlet openings 143 and 144.

The mentioned rotation of the rotary piston 66 ensures the same rotation of the rotary piston 67. In the rotational position shown in FIG. 5, the rotary piston 67 has the inlet areas 37 and 37 through the suction openings 26 * and 25 "by sucking in the necessary fuel air
mixed filled. On the other side of the cam 135 or 136, a compression process has just ended, with the fresh fuel-air mixture from the previous rotary cycle being pressed into the antechambers 97 and 98 and from there through the outlet openings 145 and 146 into the combustion chambers 111 and 112. As the rotation continues, the cams 135 and 136 pass the respective radially movable sealing elements 116 and 117, sliding over the suction openings 26 * and 25 ', so that the cam 135 with the radially movable sealing element 117 and the cam 136 with the radially movable sealing element 116 form a closed compression chamber 37 'or 37. A further rotation of the rotary piston 67 then presses the fuel-air mixture into the antechambers 97 and 97.

A motor according to that shown in FIG. 13 is very similar to a device according to FIGS. 3 to 5 Embodiment constructed. However, in this engine, the hot area and cold area are not separated, but combined with each other. In the motor according to FIG. 13, a rotary piston 61 is non-rotatably arranged on the axis of rotation 15.

net, the inside serving as an antechamber 96 Has cavity. The rotary piston 61 is arranged in a housing 21 which has a circular cylindrical cross section and has stationary sealing areas 94 and 95 at diametrically opposite points in which radially movable sealing elements 131 and 132 are arranged. These radially movable sealing elements 131 and 132 1iegen on the outer surface of the rotary piston 61, which in turn in a diametrically opposite arrangement, the cams 137 and 138, which are held by the radially movable sealing elements 132 and 131 can be driven over during a rotary movement.

The housing 21 has a suction opening 32 'at the end in the vicinity of the radial sealing element 132 and in the vicinity of the radially movable sealing element 131 has an overflow opening 32. Furthermore, on the second page of the radially movable sealing element 132, the outlet opening 154 is provided. On the second side of the radially movable Sealing element 131, an overflow inlet 35 and the ignition device 9 are provided.

The overflow opening 32 is connected to the antechamber inlet 33, while the antechamber outlet 34 with the overflow inlet 35 is connected.

In the arrangement shown in Figure 13-15 is the Combustion chamber 110 from the antechamber 96 via the antechamber outlet 34 and the overflow inlet 35 have just been supplied with compressed fuel-air mixture, wherein in the in 13 of the rotary piston 61 the antechamber outlet 34 leave the overflow inlet 35 has so that the antechamber outlet 34 is now closed is. The antechamber inlet 33 has the overflow opening 32 not yet reached in the end face of the housing 21.

In the rotary arrangement shown is now carried out via the Ignition device 9 the ignition whereby the rotary piston 61 is rotated in the direction of arrow 164. Ln the shown In its rotational position, the cam 138, together with the radially movable sealing element 131, closes the fuel-air mixture filled compression chamber 113 and presses this fuel-air mixture in the course of the further rotation through the overflow opening 32 via the antechamber inlet 33 into the antechamber 96. At the same time, fresh mixture is drawn on the other side of the cam 138 via the suction opening 32 ' sucked into the inlet area 42.

Burned gases from the previous work cycle are simultaneously released from the combustion chamber 110 facing away from the side of the cam 137 through the outlet opening 154 pushed out completely. Ks therefore takes place in each case an ignition after half a turn.

The radially movable sealing elements 131 and 132 can be used in the radial direction to generate the sealing pressure e.g. acted upon by leg springs 165 or by gas pressure. In the latter case, the elements 131 protrude into one Pressure chamber 166, which is supplied with pressure via a throttle 167, e.g. from combustion chamber 110.

The arrangement described for FIGS. 13-15 has the advantage of a very compact design and at the same time allows a The rotary piston 61 is cooled by the fuel-air mixture in the antechamber 96.

It is also possible to use the engine according to FIGS. 3 to 5 with a rotary piston designed as a hollow body the manner described for Figure 13 to equip.

It is also possible to seal the cams of the respective rotary piston against the inner wall of the housing not to be caused by a physically fitting and rubbing sealing strip, but by the fact that the respective Gap is kept as small as possible and with coming from the respective antechamber compressed fuel-air mixture is filled with a radially directed flow direction via corresponding nozzle strips. The direction of rotation of the rotary piston ensures that the fuel-air mixture exiting at these points in the combustion chamber 110 flows off and is afterburned there, so that this even results in an improvement in torque of the engine.

A motor structure according to FIG. 16 corresponds in its functional principle the embodiments described so far, in particular an embodiment according to Figure 13. It however, the structural design is changed so that the sealing problem is simplified.

A motor according to FIG. 16 also consists essentially of a housing 192 with an essentially cylindrical one Housing interior 174, a shaft 189 rotatable concentrically with this housing interior 174 in the housing is mounted, on which a rotary piston 177 is rotatably arranged. The rotary piston 177 points radially in itself opposite arrangement, two sealing areas 168 and 169, in the shape of a tooth of a gear with tooth flanks curved in the form of an involute in the exemplary embodiment. The end faces of this tooth-shaped Sealing areas 168 and 169 are designed so that they approximately against the inner wall of the housing interior 174 can seal in the manner as already described for the previous exemplary embodiments.

The housing 192 also has two cylindrical chambers 193 in a diametrically opposite arrangement and 194, in which sealing rollers 172 and 173 rotatably

ό ό Z I Z 7 U

each on a shaft rotatably mounted in the housing 190 and 191 are arranged. The shafts 190 and 191 mentioned here run parallel to the shaft 189. Between the cylindrical outer surface of the seal rollers 172 and 173 and the corresponding cylindrical inner surface the associated cylindrical chambers 193 and 194, the narrowest possible gap is provided as a seal. However, this seal can also be achieved by other means. The aforementioned sealing rollers 172 and 173 each have a tooth gap 170 or 171, which in the corresponding rotational position with the tooth-shaped Sealing areas 168 and 169 work together and their flanks for this cooperation in a suitable manner are shaped.

The shafts 189, 190 and 191 can be connected to one another, for example via spur gears, so that when a corresponding rotational movement of the rotary piston 177 and the rotational movement of the sealing rollers caused thereby 172 and 173, the tooth gap and tooth always come together.

In the rotational position shown in FIG. 16, the tooth-shaped sealing areas 168 and 169 work together with the associated tooth gaps 170 and 171 of the housing interior 174 divided into an inlet and compression area 175 on the one hand and an expansion and discharge area 176 on the other hand. The area 175 has an inlet opening 183 on the end face in the vicinity of the sealing roller 173 for the inlet of fresh gas. The area 175 also has an overflow channel 181 at the end in the area of the sealing roller 172, which in the Embodiment via a connecting line 188, in the course of which a prechamber 178 is arranged, is connected to an inlet opening 182 which is at the end face opens in the vicinity of the sealing roller 172 in the expansion and outlet area 176. Near the inlet port 182 an ignition device 187 is also provided.

In the area of the sealing roller 173, the area 176 also has an outlet opening 184.

If the rotary piston 177 continues to rotate in the direction of arrow 195 from the rotational position shown in FIG. so the tooth-shaped sealing area 169 runs over the inlet opening 183 and thus closes the area 175 against this inlet opening 183. In the further course of the rotation, the tooth-shaped sealing area now pushes 169 the one in area 175. Fresh gas together and via the overflow channel 181 through the opening Check valve 179 in the antechamber 178. The inlet opening 182 is still from the body of the rotary piston 177 closed, but the tooth-shaped sealing area 168 also migrates out of the tooth gap 170, which in turn disappears in the cylindrical chamber 194. In the further course of the rotation, there is then an end face on the rotary piston

177 provided recess 185 over the inlet opening 182, so that now fresh mixture from the antechamber

178 enter the expansion space formed between the sealing roller 172 and the tooth-shaped sealing area 178 can. In the space mentioned there is then compressed fresh mixture, which is now ignited via the ignition device 187 can be. The expansion pressure of the burning fresh mixture is based on the one hand on the Sealing roller 172, which now rolls on the outer circumference of the rotary piston 172 and in line contact with it stands and on the other hand on a flank of the tooth-shaped sealing area 168, whereby this and thus the rotary piston 177 can be rotated further in the direction of arrow 195. On the other . Side of the tooth-shaped sealing area 168 simultaneously becomes the existing one from the preparatory work cycle burnt gas expelled through the outlet port 184. The line contact between the sealing roller 173 and the circumferential surface of the rotary piston 177 ensures that no burned gas enters the area 175 entry.

- 3ΈΓ -

After a rotation of 180 ° from the rotary position described at the beginning, the tooth-shaped sealing area is 169 migrated upwards with the front-side recess 186 assigned to it and the work cycle described starts all over again. The check valve 180 still provided in the connecting line 188 prevents this definitely a flashback of the explosion flame into the antechamber 178.

It is of course also possible in the case of an engine according to FIG. 16 to have the prechamber inside the rotary piston 177 to be arranged, as already described for Figure * 13.

It is also important to note that the invention Motors can also be operated as pumps. It then forms the respective overflow channel and the Outlet channel a pressure chamber outlet. The inlet ducts retain their function or serve as a suction line. Ignition device and antechamber can be omitted.

List of the reference symbols used

1 - 9 Ignition device 10 - 15 Axis of rotation 16 - 23 casing 24 Inlet port 25th - 32 Be rs t opening 2 B' - 32 ' Suction opening 33 Vorammereiη1aß 34 Eat out the front chamber 35 Overflow inlet 36 - 42 Inlet area 43 Exhaust port 44 - 51 Outlet area 52 - 55 Sealing element 56 - 59 Sealing area 60 - 67 Rotary piston 68 - 71 Combustion chamber 72 - 79 Firing channel 80 - 95 stationary sealing area 96 - 104 Antechamber 105 - 112 Combustion chamber 113 Compression room 114 - 132 radially movable seal 133 - 138 cam 139 compressor 140 Compressor. 141 engine 142 engine 143 - 154 Outlet opening 155 arrow 156 Backdrop 157 arrow 158 Beginning of the antechamber 159 End of the antechamber 160 Limitation ^ 1i η ie 161 - 164 PViii I

Δ Ι Z / U

- StT -

165 leg spring

166 printing room

167 thrush

168 sealing area

169 sealing area

170 tooth gap

171 tooth gap

172 sealing roller

173 sealing roller

174 Housing interior

175 Inlet and Compression Area

176 Expansion and exhaust area

177 rotary lobes

178 antechamber

179 check valve

180 check valve

181 overflow duct

182 inlet port

183 inlet port

184 exhaust port

185 recess

186 recess

187 ignition device

188 connecting line

189 wave

190 wave

191 wave

192 case

193 cylindrical chamber

194 cylindrical chamber

195 arrow

- blank page -

Claims (1)

Protection claims 1.) Rotary piston engine with an ignition device, at least a housing arranged concentrically to an axis of rotation with inlet and outlet channels and at least one Rotary piston arranged concentrically to the axis of rotation, which has circumferential sealing areas for sealing against has the inner wall of the housing, characterized in that the housing (17-23) in the direction of rotation has stationary sealing areas (80-95) to delimit spaces of different functions and that at least one antechamber (96-102) and openings (25-31 and 35) for transferring the compressed medium into the Combustion chamber (103-110) are provided. 2. Rotary piston engine with an ignition device, at least one arranged concentrically to an axis of rotation Housing with inlet and outlet channels and at least one rotary piston arranged concentrically to the axis of rotation at least radially acting and movable sealing elements, characterized in that the sealing elements (52-55) in the rotary piston (60) at four sealing areas (56-59) evenly distributed in the circumferential direction are provided, in the rotary piston (60) between the sealing areas (56-59) each one radially outwardly open Combustion chamber (68-71) is provided with combustion channels (72-79) emerging approximately at the sealing areas (56-59) is and wherein the housing (16) in the circumferential direction in four in each case the distance between two adjacent Sealing areas (56-59) comprehensive zones is divided, of which a first zone between the one (24) and Outlet channel (43) and one of these diametrically opposite 332-270 -X- The second zone sealingly rests against the circumference of the rotary piston (60), while a third and one of these diametrically opposite fourth zone forms a radial distance from the rotary piston (60), the third Zone (36) in the direction of rotation at the beginning with the inlet channel (24) and the fourth zone (51) in the direction of rotation at the end is connected to the outlet channel (43) and wherein in the area of the second zone the ignition device (1) is provided. 3. Device according to claim 1, characterized in that the antechamber (97-104) simultaneously as a connection is designed, which the combustion chamber (105-109, 111,112) with the devices for delivery of the compressed medium. 4. Device according to claim 3, characterized in that the antechamber (96) in the correspondingly hollow Rotary piston (61) is provided, the antechamber (96) being connected to the combustion chamber via a slot control (110) on the one hand and with a compression space (113) on the other hand. 5. Device according to one or more of claims 1, 3 and 4, characterized in that the sealing areas on the one hand as radially movable sealing elements (114-132) and on the other hand as cam-shaped sealing areas (133-138 and 84-93) are designed with a sealing zone. 6. Device according to claim 5, characterized in that the radially movable sealing elements (118-130) in the rotary piston (62-67) and the cam-shaped sealing areas (84-93) are arranged in the housing (18, 23, 19, 20). 7. Device according to claim 5, characterized in that the radially movable sealing elements (114-117, 131,132) in the housing (17, 22, 21) and the cam-shaped sealing areas (133-138) are formed on the rotary piston (61,66,67). 8. Device according to at least one of claims 1 and 3 to 7, characterized in that each is diametrically opposite at least two radially movable sealing elements (114-121) and at least two cam-shaped Sealing areas (84-87, 133-136) are arranged, two such devices (140,142; 139,141) rotatably on the same axis of rotation (11,12) act and one as a compressor (139,140) and the other as a motor (141,142) is working. 9. Device according to at least one of claims 1 to 8, characterized in that the housing (17, 22, 18, 23, 19, 20) in the direction of rotation closely adjacent and arranged in pairs (25, 26 ', 25, 26, 27, 28', 27, 28, 29 ', 30', 31 ', 32') and outlet openings (143-154) which via a sealing element (84-88, 90, 92, 131, 132) sealing the rotary piston (61-67) from one another ■ are separated. 10. Device according to claim 9, characterized in that the rotary piston (63) is evenly distributed over three arranged sealing elements (122-124) against the inner wall the housing (19) seals and that in the direction of rotation of the suction opening (29 *) an inlet area (39), a stationary sealing area (89), an outlet area (48), an outlet opening (151) and a stationary sealing area (88) follows. 11. Device according to claim 10, characterized in that 3 3 2 I Z / U the rotary piston (62) has six sealing elements (125-130) in the arrangement described and that the in Claim 10 described areas of the housing in the direction of rotation in the sequence described repeat once. 12. Device according to claim 10, characterized in that the number of sealing elements of the rotary piston multiplies wherein the areas of the housing described in claim 10 in the described order are also multiplied by the factor of multiplication. 13. Device according to claims 1 to 12, characterized in that the inlet and outlet channels to the End faces of the housing are provided. 14. Device according to at least one of claims 1 to 13, characterized in that the circumferential direction successive rooms are separated from each other by sealing areas of the housing. 15. Device according to one of claims 1 and 5 to 14, characterized in that the inner wall of the housing (17,22) has a circular cylindrical cross-section and in the housing (17,22) radially movable sealing elements (114-117) is sealed against the circumferential surface of the rotary piston (66,67), the rotary piston (66,67) in the circumferential direction cam-shaped sealing areas (133-136) for sealing against the circular cylindrical inner wall of the housing (17, 22). 16. Device according to one of claims 1 and 3 to 15 characterized in that the cam-shaped sealing elements elements as a sealing zone have at least radially directed openings to supply at least the gap between the inner wall of the housing and the nearest counter surface of the rotary piston with compressed medium. 17. Rotary piston engine with an ignition device at least a housing arranged concentrically to an axis of rotation with at least inlet and outlet channels and at least a rotary piston arranged concentrically to the axis of rotation with radially extending sealing areas for sealing against the inner wall of the housing after at least One of Claims 1 to 16, characterized in that the sealing areas (168, 169) are tooth-shaped with rolling flanks are formed, each tooth-shaped sealing area (168, 169) having a corresponding Tooth gap (170, 171) of rotatably mounted sealing rollers (172, 173) to subdivide the interior of the housing (174) cooperates in the inlet and compression area (175) and in the expansion and outlet area (176). 18. Device according to claim 17, characterized in that the sealing rollers (172, 173) with constant translation are driven to the rotary piston, the translation being designed so that an incoming tooth (168, 169) can work together with an incoming tooth gap (170,171). 19. Device according to at least one of claims 1 to 18, characterized in that each prechamber (178) over a check valve (179) blocked against backflow into the compression chamber (175) ii! t. 20. Device according to at least one of claims 1 to 19, characterized in that each combustion chamber (105-112) or the expansion and outlet area (44-51, 176) via a check valve (1-80) against backflow is locked in the antechamber (178).