DE2608479A1 - Cylindrical casing type rotary IC engine - has rotating discs in intersecting planes forming working spaces with varying volumes - Google Patents

Abstract

Engine has a cylindrical casing (11), and a rectangular plate (22) revolves on the axis of the cylinder dividing it into two halves. It carries two circular discs (33) at its ends which are perpendicular to it and to the cylinder axis and contain the inlet and discharge ports (12). A circular disc (44) is held across the cylinder at an angle to the cylinder axis. It can revolve in an inclined groove (6) in the cylinder wall and has a central slot through which the rectangular plate (22) passes. Rotation of the latter therefore causes rotation of the inclined disc in its guiding groove. The rotation of the plate and disc causes the spaces (7, 8, 9, 10) formed between them and the cylinder walls to vary in volume.

Description

K A M M E R M O T O R - K A M M E R P U M P E

The invention relates to a novel embodiment of a pre-combustion engine or a chamber pump.

The best-known embodiments of internal combustion engines are the Piston engine, the Wankel engine and the orbital engine. Common to all of these engines is the generation of a rotary movement with the help of one or more eccentrics the usual piston engines in the form of the crankshaft, in the Wankel engine in the form of a centrically rotating "rotary piston" and in the orbital motor in the form of a pure translational, eccentric moving disc ("eccentric piston").

The previously known methods for generating a rotary movement the increase in volume of a closed volume when expanding an enclosed volume Work releases have a number of disadvantages. The night oils are well known The main disadvantage of the piston engine is the complex crankshaft, it requires a complex manufacturing process with the correspondingly high manufacturing costs. In the case of defects in individual parts or parts of the crankshaft, it is usually the case necessary to completely renew this complicated and expensive component. Ebonso from The disadvantage is the back and forth movement of a large number of individual parts (piston, connecting rod, Valves, tappets, etc.). It leads to increased wear and tear and reduced conversion the enerGy released from the working gas in Rotational energy. A functioning piston engine requires many individual parts and the amount of material and the production costs are therefore very high.

Complicated and the corresponding disadvantage of the Wankel engine is the creation of the complicated combustion chamber and the sealing surfaces and lasts. The sealing problems with these engines mostly lead to bostestanding excessive wear and tear and limited service life.

Due to the back and forth movement of individual parts or dio eccentric Movement of the "rotary piston" or the "eccentric piston" occurs in the piston engine, Wankel engine and orbital motors cause adverse vibrations and shaking movements.

Through the back and forth movement and / or eccentric movements Larger masses are severely limited the number of revolutions in the motors mentioned.

Wankol engine and orbital engine allow the construction of the engine compartment not to produce embodiments with arbitrarily high compression ratios.

The specified defects are also present in pumps that are based on the same Construction principles are built.

The listed-disadvantages and deficiencies are in the invention Engine or the pump according to the invention avoided. This is the purpose of the Chamber of Labor - In the engine the combustion chamber or expansion chamber, in the pump the pump chamber -Invention designed so that they "penetrate" surfaces from each other or partial areas of at least one area with rotational symmetry, at least a surface rotatably arranged about the axis of symmetry and at least one further, Limed surface rotatably arranged about an axis inclined to the axis of symmetry where surfaces "penetrating" one another either slide on one another or an area in recesson receding in the other area 0 To a functioning motor or pump and a working chamber formed in this way only a few individual parts are necessary, resulting in significant advantages compared to the previously common engines such. B. s material savings low manufacturing costs low maintenance costs.

The following advantages also result: very smooth running less Wear high operational safety long service life compact design.

An arrangement with a working chamber according to the concept of the invention can be used as a single-chamber pump or as a single-canine meter.

In an advantageous embodiment of the device according to the invention if several chambers are already enclosed by the same rotationally symmetrical surface, which in the course of the rotary movement have the same surface areas of the station-symmetrical Make use of the area.

An embodiment with a motor or engine that can be easily stolen.

The pump chamber has working chambers that cover the following areas or Bodies are limited: by the surfaces of a perpendicular.

circular hollow cylinder, one around inside the cylinder with the partition wall rotating along the cylinder axis and sliding on the cylinder inner surface flat surfaces, 2 circular disks attached to the end faces of the partition wall and flat semicircular disks passing through the rotating partition with be set in rotary motion, with their straight cattle on the flat surfaces the partition wall slide and the semicircular edges in an inclined to the cylinder axis be guided in the groove machined inside the cylinder wall.

For the technical design of the motor or pump according to the invention it is useful if the inclined to the axis rotating discs from 4 individual Half-disks are formed.

An advantageous variant of the embodiment with 4 Ilaib slices has a compensation for the half-disks generated during operation.

In a particularly advantageous embodiment of the invention Motor or the pump according to the invention, the working chambers are formed by the space between a concave spherical surface, 2 flat surfaces of two circular disks and the cylindrical surface of a cylindrical intermediate piece.

A variant of the embodiment with a spherical motor or

Pump room with additional advantages is characterized by rigid cylindrical spacers connected to an inner motor wall.

In the case of the spherical engine compartment, the individual Half slices formed into a single circular disk provided with a recess will.

The embodiments with spherical engine compartment allow of the Construction of the working chamber to realize any compression ratio.

For di. technical application of the device it is appropriate to the rotating To guide discs and shafts in ball bearings or roller bearings. One embodiment has an adjustable roller bearing that is also advantageous for large dimensions.

An embodiment with a very simple cooling and lubrication system is equipped with channels and spaces in the rotating discs and places, dio are designed so that gases odor liquids due to the in operation the forces acting on them are conducted through the inner engine parts will.

It brings huge amounts of money for the operation of the engine according to the invention Advantages entail when the inlet ports, the outlet ports and the devices are arranged in rotating chamber walls to control the inlet and outlet times, and the working gas through channels in the rotating winches to and from the chambers. is diverted away from the chambers.

In an embodiment with conventional valves for controlling the Inlet and outlet processes are controlled by arranging the valves in a rotating manner Chamber wall nouo, for these valves in common engines not crziolbaro'Epigenskllaften achieved.

Preferred embodiments have a particularly simple control the inlet and outlet processes with perforated disks, which are dor by cams on the circumference Discs and fixed cams are moved in the housing.

In an advantageous control of the inlet and outlet processes the unused working gas and the used gas through one and the same opening guided in a rotating chamber wall, utilizing the given rotational movement is, used and unused working gas in spatially separate channels lead to or away.

In another advantageous variant of the control with perforated disks are used to open and close the inlet and outlet ports of all chambers as a whole only 4 perforated disks of the same construction, each with a valve hole, are used.

An effective filling and emptying of the Arboitskammorn is in one embodiment with spirally gelcrunmltens in rotating chamber walls arranged inlet and outlet channels.

In an advantageously further developed embodiment with spiral curved inlet and outlet channels are the times of opening and closing the inlet and outlet openings are chosen so that both openings simultaneously for a short time are open.

An embodiment is advantageous for technical production in which the housing is formed from 2 completely identical halves.

In the following, the principle and details of the invention are given explained in more detail by sketches.

The figures are numbered so that for one and the same embodiment the same figure is used in each case, but with different sub-numbering for the individual part drawings. In the various embodiments will be Corresponding parts are provided with the same symbols.

Invisible edges or edges that are unnecessary for understanding omitted for the sake of clarity of the drawing.

The elements that make up the working chamber are designated as follows: the axis of rotation: O the surfaces with rotational symmetry: 1 the surfaces forming these surfaces Solid of revolution: 11 the surface (s) arranged to be rotatable around the axis of rotation: 2-, 3 the bodies forming this surface: 22,33 those inclined to the axis of symmetry arranged surface (s): 4 the bodies forming this surface: 44 It show: Fig. 1.1 - 1.11 an advantageous embodiment in which the surface with Rotational symmetry (1) formed by a vertical, circular inner cylinder will.

1.1 an exploded view with the most essential parts, disassembled shown engine resp.

PUMP INNER PARTS.

1.2 shows a perspective illustration with the cylinder open 1.3 is a schematic diagram of the section through the axis of rotation (o3 and perpendicular to the inclined surface (4) runs at the time of the movement sequence in which the partition (22) is just perpendicular to the plane of the drawing.

1.4 a section through the axis of rotation (0) perpendicular to the inclined Surface (4), with the partition (22) and the inclined surfaces compared to Fig. 1.3 (4) have been turned by 900 in the cylinder housing (11).

1.5 shows the section AB indicated in FIG. 1.4 through the axis of rotation perpendicular to the partition (22).

1.6-1.11 construction details of this embodiment.

Fig. 2.1 - 2.7 a particularly advantageous embodiment in which the surface with rotational symmetry (1) is formed by a concave spherical surface.

2.1 an exploded view of the essential one-time parts.

2.2 shows a perspective illustration of this particularly preferred one Embodiment with a cut-open ball.

Fig. 2.3 Section through the axis of rotation (O) perpendicular to the inclined surface (4), at the moment of flexing, in which the partition (22) is perpendicular to the plane of the drawing stands.

Fig. 2.4-2.7 construction details of this embodiment.

3.1 and 3.2 advantageous variants of embodiment 2.

The way in which the device according to the invention works is illustrated in FIG. 1.2 - 1.5. explained, initially in the mode of operation as a pump.

That of the surface (i) of the inner cylinder, the flat surface (2) the one arranged to be rotatable about the axis (o) of the cylinder and sliding on the cylinder surface Wall (22), the inwardly directed surface (3) of the circular disk (33) and the inclined to the axis arranged surface (4) enclosed. Volume forms a working chamber. A drive from the outside causes the wall (22) to rotate about the axis (O) offset. The half-disks (44) are rotated by the partition (22) offset, ge leads in a groove (6) that is inclined to the cylinder axis Level is incorporated in the cylinder inner wall.

The edges (4 ') of the half-disks (44) slide on the flat Surfaces (2) of the partition (22). During this rotation, the changes Size of the enclosed volume of the Working chamber periodically. If one follows the volume designated by (7) in the moment of movement of Fig. 1.3, so its size is about half a turn of the partition wall (22) in advance Axis (o) under continuous enlargement (7 ') over into the one marked (8) Volume. With the subsequent half turn, the chamber volume is reduced again (7 '') on the original word (7). Volume (7) is the smallest chamber volume, Volume (8) the largest chamber volume occurring in the course of the threat of the partition. In cooperation with openings (12) in the disc (33), which are in the advance of a oino Kallmlor acts as a Pump for gases or liquids.

In the advantageous embodiment according to FIGS. 1.1-1.5 are enclosed by one and dorselbov cylinder inner surface 4 chambers (7), (8), (9), (10). With each Kammor, the volumon changes in the course of a full revolution the same regularity, with each 2 chambers increasing in volume at the same time or show a decrease in volume. The amount of the increase in volume is exactly the same the amount of the decrease in volume of the adjacent chamber. The by the movement of the Volume changes caused by partition are such that the sum of the volumes of the respective neighboring chambers does not change.

In this embodiment, the device according to the invention can be used as a 4-chamber pump, or with a suitable series connection of the individual chambers as a Mohrstufon pump be used.

When working as a motor, the chambers serve as expansion spaces. DL: '. h appropriately controlled openings is the working medium, for example woise a combustion gas, sucked in or expelled. The beginning of the work cycle is at the volume size (7). The increase in volume when expanding the enclosed Arboitsmediums leads to a continuous transition of the chamber volume from the dor Size (7) through (7 ') to size (8). In doing so, the expanding medium forces exerted on the partition wall (22) which lead to oinor rotational movement of the partition wall around the axis (o). In the embodiment with 4 enclosed by the surface of revolution Chambers, the device according to the invention can be used with advantage as a 4-stroke engine. The changes in volume of the chambers are such that the 4-stroke procedure is used when working One work cycle can be carried out for every half engine revolution. At the time of the sequence of movements on which Fig. 1.3 is based, the 4 chambers (7) up to (10) for example at the beginning of the following bars: (7): intake, (8) exhaust, (9) ignition, (10) compression. There are 2 full turns of the partition (22) then the following cycles on the individual chambers: Chamber (7): suction. Compress. Ignite. Exhaust chamber (8): exhaust, suction, compression, ignition Chamber (9): Ignition, exhaust, suction, compression chamber (10): compression, ignition, exhaust, Priming After 2 revolutions, the work processes are repeated. The length of time for a single cycle is equal to the time for a half-turn of the partition (22) around the axis (O).

The movement processes taking place in this motor are almost one Rotational movements: the partition (22) performs a pure rotation around the axis (o) and the half-disk (44) moved along by the partition wall is almost a pure rotational movement (see below) about one inclined to the axis (o) and standing perpendicular on the flat discs Axis (13). The rotation of this motor is d ect, i.e. without any interposition any shafts, eccentrics or gears, due to the pressure of the expanding Gas is generated in a chamber on the rotating partition. The engine is free from any eccentric movement. There are therefore no central and oscillating movements on. This reduces the number of wear parts to a minimum, which means that energy is used becomes optimal.

With the 4-chimney version, the chambers lead after every half turn the partition wall one after the other an expansion stroke, the forces that are released in the process are delivered to one and the same rotatable wall (22).

Instead of rotating the partition, you can of course also hold the partition wall and the motor housing consisting of the rotating surface let it rotate. Nothing changes in the way the motor works.

The technical details are for the Gorät according to the invention explained in the way it works as a motor. This is done in Fig. 1.6.

Corresponding considerations apply to a device operating as a pump.

The Fig. 1.6 shows the time of the movement wioder, which is also the 1.3 is based. It shows the section through the motor axis, the vertical one on the partition (22) and perpendicular to the half-disks arranged at an angle to the axis (44) stands.

For the technical design of the engine, it is advantageous if 1.3 formed from a total of 4 individual disks (44) will. The edges of each of these half-disks are designed as cutting edges (14) with a cutting angle (15) that is slightly smaller than the intermediate angle (between Cylinder axis and groove. The sealing of the halves against the partition (22) is made by a suitably selected contact pressure of the cutting edges (14) against the wall (22) achieved. The bevel of the cutting edges is on the side facing away from the Ka-aer Half discs attached, this creates a simple seal the dor Kanimer facing flat surfaces of the ileal discs against the cylinder wall achieved (see below

For the technical design, an angle of inclination (16) of the guide groove (s) in the inner wall of the cylinder against the axis of rotation in the size of 600 - 450 expedient. The size of the angle of inclination determines the torque reserve of the motor, and together with the radius of the cylinder and the height of the door wall, the chamber volume.

The compression ratio is determined by the thickness (222) of the Partition wall (22), with increasing thickness it becomes larger; the compression ratio is independent of the inclination of the groove (6) relative to the axis (o). Additionally can the compression ratio can be increased by removing the space of Fig. 1.3 between partition (22), inclined half-panes (44) and cover plate (33) fills out. This can be achieved, for example, in the manner of FIG. 1.6. Here is in the two upper chambers the space between the partition (22) and the cover plate (33) filled in by the sections (17) and (17 ') of an ice cone of its base on the cover disk and its tip in (18). Instead, as for the both lower chambers outlined, also on the inclined discs (44) sections (19) and (19 ') of a circular cone with the tip in (20).

By a contact pressure of the half-disks that is independent of the number of revolutions (44) To ensure against the partition, the half-disks are counterbalanced Mistake. These counterweights can be attached as shown in Fig. 1.7. 1.7 shows two opposing half-disks with the fost connected Counterweights (21) each in plan and cross-section.

In the engine, these disks interlock with their counterweights and enclose the partition (22). (of which in this figure the cross-section is perpendicular to the axis (o) is shown).

The centrifugal forces can also be compensated for by a device as it is indicated schematically in Fig. 1.8. The figure shows a section from the middle of the engine with the partition (22) and the inclined half-disks (44).

Between each 2 halved disks on the same side of the partition each a gear (23) is attached, which is in corresponding teeth in the half-disks engages. Each gearwheel leads through an opening (24) in the partition wall a threatening connection to a balance weight around the axis of the gear (25) on the opposite side of the partition. About this connection between the gear axis and the centrifugal weight, when the partition wall rotates in A centrifugal forces from the balance weight (25) occurring in opposite directions and disks (44) lifted. The opening in the partition (24) lies in one area the partition, which is in the lead of the movement from the edges (4 ') of the half-panes 44 is never painted over. With compensated centrifugal force can the contact pressure of the Iialbiben against the partition wall, for example by suitable dimensioned springs (26) between each 2 half-disks, as indicated in Fig. 1 .7, determine. By appropriate choice of the largest of the mass of the balance weight or the distance between the counterbalance weight and the half-panes can also be achieved that the contact pressure changes with the speed. For example with a wet one of the flyweight, which is slightly less than the mass of the half-sole, he takes Contact pressure with increasing speed.

In order to reduce the friction, the circumferential in the groove is provided Washers (44) by ball bearings to their. 1.6 shows a possible embodiment.

Stir around the axis (o) while rotating the partition (22) the inclined half-disks sliding on the partition wall one Rotation around their axes of rotation (13) or (13 '), superimposed by a minimal backward and reciprocating on their axes (13) and (13 '), respectively, towards and away from the axes. (The The direction of this translational movement is given by the line of intersection, which is at the intersection of the surface (4) of the inclined disc (44) with the plane through the axis of rotation (o) and perpendicular to the partition (22) results). The back and forth movement has its cause in the periodically changing distance in the course of the rotary movement of the half-disks from their axes of rotation (13) or (13 ') In the sections of Fig. 1.3 and 1.5, which are made by a 900 turn of the partition wall relative to the cylinder differ, the different distances (27) and (2S) have to be observed. Dio The maximum amplitude of this periodic to-and-fro movement is equal to the difference the distances (27) and (28) and is in practical designs of motor or pump tiny. The ball bearing can therefore be designed so that the rotary movement the discs (44) is received by the ball bearings (29) or (29 ') (Fig. 0.6) and the minimal to-and-fro movement by slightly sliding the discs (44) balanced over the ball bearing mount (30) in the radial direction (the ball bearings) (as indicated by the clearance (31) in Fig. 1.6).

The rotary movement generated by the motor is picked up via a Shaft (32) which is formed around the axis (0) of the partition (22). This wave is guided by ball or roller bearings to reduce friction. Fig. 1.6 shows an embodiment with adjustable bearings (34), as by dio Mother (35) is indicated.

It is useful if the shaft and the interior are hollow the hollow shaft (36) via the opening (24) in the partition wall shown in FIG. 1.6 (22) with the space (37) between the inclined half-disks in connection stands, this cavity, formed from hollow wool and space between the inclined Discs, can be designed as a centrifugal pump for gases; the flowing through Gases can be used to advantage Cooling of the motor innonteilo related will. For this purpose, the jacket of the cylinder is provided with bores (38) and in the space between the half-disks, webs are placed on the iral disks (39), dio point in the radial direction. When the partition wall rotates, the cavity in the wool is sucked in gas, preferably air, and due to the centrifugal force, which it takes place in the space between the half-disks, through the holes in the Cylinder jacket ejected back into the outside space. With suitable training of the Cavities in the shaft, in the partition and in the space between the inclined ones Half-panes, all internal parts can be air-cooled in this way.

The same principle can be used in addition to air or instead of air also oil for the lubrication of the internal engine parts through appropriately designed channels and evaluate cavities guided.

The working chamber is sealed by resilient sealing rings and Diclitungsleiston. The seals for sealing the inclined to the cylinder axis circumferential half-disks (44) against the cylinder wall (11) are in the guide groove (6) housed the half-disks. In Fig. 1.6. Is the cross-section of these seals (40) drawn in black, the course in the one below the plane of the drawing Part of the cylinder is indicated by dashed lines. Each of these seals lies in one own fitting groove and is supported by resilient elements, e.g. a corrugated ring between Seal (40) and groove base (41) against the flat surfaces (4) of the inclined circumferential Washers (44) pressed.

For sealing the convex, sliding on the inner surface of the cylinder cylindrical surface of the partition - (2 ') in Fig. 1.1 - are sealing strips provided, the dashed lines in the rotor cross-section shown in Fig. 1.6 (42) are indicated. These sealing strips are also made up of resilient elements between the sealing strip and the groove bottom against the cylinder wall (1).

The length of these sealing strips is limited by sealing rings (43), which seal the cover plates against the cylinder wall. These sealing rings are, like the usual piston rings of the piston engine, resilient. To a uniform wear and tear as little as possible in the area covered by these rings Area, it is advantageous to place the rings in a groove, which lies in a plane slightly inclined to the axis of the axis; Fig. 1.6 shows this arrangement of the rings (1s3 ') in the lower cover disk.

The supply and discharge of the working gas to and from the arboit chambers the engine can be controlled by common, suitably mounted valves. the Using conventional valves in the engine according to the invention brings new advantages for this type of control entails that these valves are used in the known Motors do not have. An embodiment for the application of the usual Valves in the engine according to the invention is for the following embodiment: n 2.1 - 2.7 shown.

Another advantageous control of the inlet and outlet processes you get through the use of slides or perforated disks. With this control Numerous embodiments of the suction and discharge process are possible. Obvious is an embodiment in which the slides are designed so that iode and outlet opening of a chamber opened or closed by its own slide will. However, the embodiment according to FIGS. 1.9-1.11 is more advantageous.

This embodiment is characterized by suction and discharge of the working gas through one and the same opening in a rotating chamber wall take place. The separate supply and removal of unused and used Working gas to or from the opening in the chamber wall is through Use of the given rotational movement is achieved.

Fig. 1.9 shows the section CD from Fig. 1.6 again, Fig. 1.11 is the section EF of Fig. 1.6 through the engine top.

The double hatched circles (45) represent the openings (45) 1.6 through the chamber wall to the chambers below The working gas is sucked in through these openings and after combustion (through the same Opening) ejected again. The opening and closing times of an inlet / outlet port are controlled by the valve disks (46) according to Fig. 1.10. These valve discs are housed in recesses (47) of the cover plate (33) and around the axes (48) rotatably mounted (Fig. 1.6 or 1.9). The valve discs have openings (49) provided which, when prehoning the disks, revolve around their own axes, (48) completely or partially cover with the openings (45) in the cover disk. Are in "working position" the valve disks relative to the recesses in the cover disks in which they are are housed, at rest; they then rotate together with the cover disks around the motor axis. Joweils when transitioning from one engine cycle to a new cycle the valve disks move a certain angle within a small period of time rotated on their own axes. The rotation of the discs is controlled by cams (50), which are arranged distributed on the disc ring (for clarity Because of this, they are exaggerated in the drawing in the form of a sawtooth. In the technical design, cams with sufficient "soft" engagement will be selected). When rotating the partition and cover disks together with the valve disks the motor axis (o) engage the cams of the valve disks in the corresponding ones Cams (51) incorporated into the cylinder jacket and rotate the valve disks around one certain angle around their axes (4s)). This will, depending on the clock is to be carried out, the inlet / outlet opening in the deck plate is open or closed. Instead of the cams, the valve disks can also be arranged in a spiral Slits should be provided in which - in the manner of the Sa1-teser cross - an in the housing fixed pin grips. In the outlined embodiment Each valve disk has 2 openings offset by 1800 and 4 by 900 apart Cam.

A cam is attached to the circumference of the cylinder jacket.

The engagement time of the cams of the valve disc and cylinder jacket is selected so that the valve discs are rotated by 900 each. on Due to the selected cam distribution, each valve disk is therefore after each one full motor revolution further rotated 90 °. So every valve disk remains for the duration of 2 keys relative to the (moving sound) chamber wall in the same position; During the exhaust and intake strokes, the opening in the valve therefore coincides disk with the opening in the chamber wall and enables ejection and suction of the working gas, wanrond dor two subsequent cycles, compression and expansion, is opened in the chamber wall by an unbroken quadrant in the valve disc closed.

After 2 full revolutions of the motor, meanwhile one chamber all 4 cycles, each valve disc completes half a turn around its own axis. To seal the chamber against the valve disks is in the dock disks around the inlet / outlet openings each a sealing ring is provided, which against pushes the valve disks.

In this embodiment, the working gas is through cutouts (52, 52 ') in the stationary motor wall and diverted away.

Fig. 1.11 shows these recesses, those in Fig. 1.6 only schematically indicated (52) waron. The working gas becomes the through these openings Inlet / outlet openings (45) in the rotating cover disk below directed. In this embodiment, the working gas is sucked in while rotating Motor for both upper (or lower) chambers always within the same range of the cylinder jacket, in Fig. 1.11 for both chambers, for example, always within the area of the recess (52). While an inlet / outlet port (45) in the cover plate with the recess (52) in the Engine wall covers, can therefore be sucked in. The used working gas is also expelled for boido chambers always within the 'other cylinder half, in Fig. 1.11 thus always within the area of the recess (52 '); during the time in which the inlet / outlet opening (45) coincides with the recess (52 '), can therefore the exhaust ink take place. During the transition phase between exhaust stroke and The intake stroke disappears the opening (45) in the cover plate behind the unopened Split the engine outer wall. Through a partition placed on the outer wall, the is shown schematically in cross section (53), the working gas can therefore be sucked in ejected from dom spatially separated from one by corresponding channels Motor side supplied or led away on the other.

The same control process as with the specified execution of the Valve disks can also be carried out with valve disks, which are shown in 2 adjacent Quadrants each have a hole, which when turning the valve schoibon around their Axes coincide with the opening in the chamber wall. This execution of the Valve disks is also distributed evenly around the circumference of the disks Provided cams, in the cylinder wall, on the other hand, there are 2 cams at an angular distance housed from 1800. The valve discs are therefore gradually rotated In contrast to the previous one: r embodiment after every half turn dos motors; the angle of rotation during the engagement point of the cams is 90 °.

The number, distribution and engagement ^ since the cams on the valve discs and the motor housing can be varied, depending on the specific requirements one can therefore achieve a back focal length of less than 900 after every full motor revolution or 900 after each half motor amdrshungwuie in the two mentioned Embodiments, achieve and other arrangements of the holes 1 than 2 holes in 2 opposing quadrants or 2 holes in 2 adjacent quadrants in the valve disks. If the Vontile discs are of the same size, a Rotation through a small angle is also available to a smaller one standing space for the individual valve bore in the valve disc and therefore sometimes to a smaller bore diameter. Depending on the special requirements will one therefore has a valve disc with a smaller back focal length and therefore smaller to be executed Rotation or with a larger back focal length and therefore a larger bore diameter consider it advantageous.

The specified embodiment of the valve disks according to Fig. 1.9-1.10 has the advantage that the discharge and suction of the working gas in one chamber through an opening in the chamber wall and through an opening in the valve disk takes place through. This simplifies the structure of the engine. Dio valve discs themselves are thermally significantly less stressed than conventional exhaust valves because After each discharge process, the valve disc by the subsequent suction process is cooled.

This avoids fatigue of the material due to overheating. With a suitable assignment of cams and openings of the valve disks to one another can in this embodiment, the suction and discharge processes of all 4 chambers can be controlled with identical discs. The arrangement of the cams is chosen so that the further rotation of the valve disks only takes place at the beginning of a cycle. During the time the cycle is running, the disks are relative to the Recesses in which they slide, silent. Through the pressure of the working gas the inlet / outlet openings through on the valve is because, -her during the course of the compression stroke and expansion stroke no increased friction of the discs on their sliding surfaces.

When using a combustion gas, the gas is ignited 4 conventional spark plugs used. The spark plugs were used in this embodiment of the motor according to the invention most expediently through openings (54, Fig. 1.11) in screwed through the upper and lower outer wall into the partition (54 ', Fig.1.9) The ignition spark is connected to the through a recess (51C ") in the partition Work chamber. Since the spark plugs rotate around the engine axis when the engine is running, the high voltage is supplied to the spark plug either via a suitably attached one Sliding contacts or by skipping a spark to the spark plug via a suitable attached spark gap.

A preferred, particularly advantageous development of the invention The motor or the pump according to the invention is shown in FIGS. 2.1-3.2. In this embodiment, the surface (1) with rotational symmetry - in the previous one Embodiment a rotary cylinder - formed by a spherical surface. Fig. 2.1 shows the exploded view with the essential motor and pump internal parts, 2.2 shows a schematic diagram in a perspective illustration with a cut open Spherical housing and Fig. 2.3 a schematic diagram of a section through the motor axis.

The half-disks described in the previous embodiment can be used in the form given for any surface of revolution. Training of the engine compartment as a spherical surface enables a very advantageous Further training-the half-discs.

In this embodiment, according to FIG. 2.1, those of the rotating dividing wall (22) with circular disks (44) set in rotation trained (Ret that they are not directly on the flat surfaces (2) of the partition (22) slide, but on cylindrical surfaces (5) of two cylindrical spacers (55).

The two intermediate pieces are the same, they have the same shape of cylinder sections passing through a plane parallel to the cylinder axis from the cylinder were separated. The intermediate pieces equal th with the upper surfaces (5 ') for their part on the flat surfaces (2) of the partition. With oinon bolts (56) both Intermediate pieces rotatably guided around the middle of the partition wall. The thickness (57) of the spacers is, as Fig. 2.3 shows, so dimensioned that the two cylindrical surfaces parts form the surface of a cylinder whose axis (58) is in the center of the partition lies and the notor axis (0) sclmoidet. The obvious advantages of this construction are as follows: The moving half-disks lead outside of the rotation around their own axis (13) no additional periodic translation movements in the radial direction Direction more out. One can therefore, as indicated in Fig. 2.1, the 4 inclined circumferential Half-disks (44) of the previous embodiment 1.1-1.111 each with a half-disk Replace (44 ') on each side of the partition (22).

Furthermore, these two half-discs can be made by rigid pre-bindings, which reach around the partition, are firmly connected to each other, or both Half discs to a single disc rotating in the groove ("rotary disc") (66) can be formed with a corresponding opening (59) for the partition wall.

This means that the counterweights are used to compensate for the centrifugal forces superfluous. Another advantage is that this rotating disk is in a ball or roller bearings can. This will build the engine simplified even further.

The operation of this embodiment 2.1-3.2 is the same as that in the previous embodiment 1.1-1.11, the technical details differ However, in part. The essential differences are shown below using the Fig. 2.3 outlined.

The section in Fig. 2.3 through the motor axis (O) is placed in such a way that that with respect to the axis by the angle (16) inclined angeordnote Uinlaufscheilze (66) is perpendicular to the plane of the drawing, and the time of the sequence of movements is chosen so that the partition (22) is also perpendicular to the plane of the drawing.

The angle of inclination between the axis and the groove for guiding the rotating disc in this embodiment can assume a width of less than 45 °; with decreasing Angle, the torque of the notor becomes larger.

The compression ratio is determined by the thickness of the partition (22), the disc (66) in the guide groove and set by the angle of inclination (16). As with the engine described in Section 1, the compression ratio can also be by filling the space between the partition (22), the rotating disk (66) and the spherical surface (i) be influenced. If necessary, this space can be filled in completely, up to the value zero of the remaining chamber volume (for the in the course of the rotary movement smallest chamber volume occurring). In this embodiment of the invention Motor, any compression ratio values can be implemented.

The rotary movement is picked up in embodiment 2 again Via a shaft that is formed around the axis (o) and through the motor housing Ball bearing odor is guided by adjustable roller bearings (35).

Resilient sealing strips and are used to seal the working chamber Circular rings related. The cross-sections of these sealing elements are shown in FIG. 2.3 to see. The rotating disk, which is inclined to the motor axis, is made up of 2 rings (6o), which lie in a pafin groove in the Ifugell jacket and are flat against the dio Press the surfaces of the rotary disk. Due to the advantageous spherical shape dos Elotorraums these seals are circular. Dio on the inner spherical surface (1) of the housing (11) sliding surface (2 ') of the partition wall (22) is convex spherical educated. To seal these surfaces that slide on one another against one another contains the partition (22) 2 grooves for receiving the sealing rings (61), the resiliently place press the inner spherical surface. The rotating disk inclined to the axis is for sealing against the cylindrical spacers with straight sealing strips (62) provided, the resilient, for example with the help of corrugated spring strips between Sealing strip and groove base, against the cylindrical surface of the intermediate piece be pressed. The cylindrical spacers are also provided with the same sealing strips (63) provided for sealing against the flat surfaces (2) of the partition (22). the The end faces of these cylindrical spacers are because they are on the inner spherical surface slide, convex spherical. For sealing against the spherical surface Housing are circular fitting grooves in these convex spherical end faces appropriate; in Fig. 2.3 the position of this groove (64) is indicated by dashed lines. These grooves take on seals in the form of an arc of a circle, which are resilient against the dio Press the inner spherical surface of the housing.

All surfaces to be sealed against one another in this embodiment to have the following common features: The bodies moving against each other slide along extensive surfaces on top of each other, i.e. the surfaces involved in the seal they have the same curvature as the surfaces. So obono surfaces slide on flat surfaces, convex cylindrical surfaces and concave cylindrical surfaces convex spherical surfaces in concave spherical surfaces. The curvature of each surfaces to be sealed against each other is in the entire, during the movement detected area of the surfaces stots the same.

Due to these prerequisites, the seal of the chambers can through simple sealing elements - sealing rings or sealing strips - are carried out, which lie in grooves which are machined into one of the surfaces involved in the seal are. The sealing elements always press vertically with their sealing surface (or always in the same direction) on the opposite one on the seal involved surface. With this type of seal, high compressions are possible.

These requirements do not apply to the rotary engine and orbital engine full; in these motors, bodies have to be sealed against each other, which are not slide on each other with extended surfaces, but only along narrow surface strips touching each other, sliding on each other. The resulting sealing problems do not occur in the engine according to the invention.

The rotating disk, inclined to the motor axis, which in this particularly advantageous embodiment of the engine according to the invention only one r executes a rotary movement about its axis (13) to reduce friction guided by rolling or rolling. In Fig. 2.3 one possible implementation is shown: bolts (65) are evenly distributed over the circumference of the motor housing (11) Motor housing attached. Conical rollers run around these bolts so that they can rotate Tread (67).

Over running surfaces (68) on the top and bottom of the circumferential disk the rotating disc is guided. To this leadership both in radialor direction The axis of the disc, as well as in the direction perpendicular to it, are to be ensured the running surfaces on the rotating disk are also designed as conical surfaces.

As indicated by the mother, the reels are adjustable in their game. Instead of sliding around the bolts, they can also be guided around the bolts in ball bearings will.

An advantageous variant of the positioning of the rotating disk with rollers is obtained by turning the part of the motor housing that carries the bolts into one forms a ring (G9) that is detached from the housing, and a running surface outside the dome in the motor housing (68 ') for the rollers around the motor housing. This arrangement from ring and individually adjustable rollers forms with the running surfaces on the rotating disk and a high-precision roller bearing in the motor wall, which is advantageous for large Rolls and bearings can be used. When manufacturing the rollers the diameters do not necessarily all have to be exactly the same, minor differences in diameter can be compensated for by the adjustment option given for each roller so that the precision of the bearing is not affected.

The adjustment process for the adjustable roller bearings is very simple carry out: the rotary disc is first replaced by precise spacers or Feeler gauges placed in the position required for engine operation. After that, the nuts are put on the bolts (or equivalent adjustment devices) tightened, preferably with a sensitive torque wrench, until all of the rollers Press against their running surfaces with the same pressure.

The exact setting is now complete.

Conventional ones are used to control the inlet and outlet processes Valves or slides, preferably perforated disks, are used. It has numerous advantages with itself when the valves or perforated disks in the rotating Umlaufscheibc des Engine according to the invention are attached, and the working gas through channels in the Circulating disc is directed to the valve bores of the chambers.

When using the usual valves in the engine according to the invention can Such an arrangement gives these valves new, advantageous properties achieve which are not given when used in conventional engines. Fig. 2.4 and 2.5 show a possible arrangement of the valves in the rotary disc.

FIG. 2.4 corresponds to the section shown in FIG. 2.3; However, the drawing is rotated so that the rotating disk (66 horizontal and the Motor axis (o) is inclined in the drawing.

Fig. 2.5 shows the section AB dor Fig. 2 through the rotary disk in the level of the valves again. The section on the left in the drawing of Fig. 2.4 shows the section CD rotated in the plane of FIG. 2.5 through 2 inputs or Outlet valves for the respective chambers located above and below the rotating disk.

The valves are arranged so that the valve stem (70) in radial The direction of the Ulnlaufscheibe, the end of the valve valve points in the direction away from the axis of rotation, and the valve disk (71) points towards the axis, when the valve is open The gases flow through a trough (72) in the rotary disk around the valve disk around into the chamber. The gas is fed in and out through channels (73) in the rotating disk. The valves can be opened, as usual, by appropriately arranged Cam closing are carried out by a return spring (75).

Due to the radial arrangement, the valves experience the rotation when the Orbiting disc has an outwardly directed centrifugal force. This increases the contact pressure When the valves are closed, the valve plate increases the size of the valve seal therefore improved. The centrifugal force also supports the restoring force of the spring during the closing process of the valves. Since the centrifugal force with the Drohzalil grows, Or, with increasing speed, there is a greater restoring force; the valves are therefore closed the faster the higher the speed. The decisive one Disadvantage of the valves in conventional engines that the valves are given due to it Restoring force dor Fcdor no longer close fast enough in the high speed range and thereby limit the speed, is used when using the usual Valves avoided in the engine of the invention. The one that grows with increasing speed Restoring force soret here that even with the highest number of revolutions dio valves close properly. The return spring in this valve arrangement in the invention The engine only has the task of closing the valves in the lower speed range, it can therefore be dimensioned weaker than usual.

Control disks can be used to control the valves themselves, dio iii correspond in their structure to the valve disks of embodiment 1.10. Only instead of the bore of the valve clioibon, a cam-like one is used in these control disks Elevation provided. The control disks are in recesses (76) in the rotary disk arranged so that their axes of rotation (77) in the radial direction of the rotary disc lie and the cam-like elevation when turning these control disks around their own Axes (77) presses against the end of the valve stem. This will during the time during which the bump on the disc and the valve stem end are in engagement, the valve opened. There are cams on the circumference of the control disks themselves, which engage in corresponding cams in the stationary engine casing, and thereby the control disks Turn further by the desired increment while the rotating disk is rotating.

Boi use of valve discs to control the inlet and outlet processes, similar to those in the embodiment 1.1-1.11 is achieved over the usual Valves have the advantage that fewer individual parts are required to control the processes are. The valve discs also have a longer service life on, because they have been mechanically and thermally less stressed.

The valve disks dor embodiment 1 dos engine according to the invention can also be used in this embodiment with a spherical engine compartment. Additional advantages are achieved by the following arrangement according to FIGS. 2.6 and 2 7. The two figures give, like the last two figs. 2.4 and 2.5, a section through the motor axis or below the section AB through the rotating disc again.

In the embodiment according to Fig. 2.6 and 2.7 are to control all Inlet and outlet processes 4 valve disks (78) are provided, which are inserted into recesses (79) the rotating disk are housed.

A single valve disc opens and closes the inlet port (80 or 80 ') and the outlet opening (81 or

(81 ') of a chamber. Each valve disc has 1 gauge, size and location are chosen so that the hole in the valve disc with the inlet port (80) or (80 ') and the outlet opening (81) or (81') in the rotary disk to cover come when the valve disc is rotated about its axis (82). The inlet and Outlet openings in each of two chambers are in the rotating disk in the form of 2 through-holes (80, 81 or 801, 81 ') and with respect to the axes of the valve disks (82) arranged at an angular distance of 90 ° to each other. In the course of the rotary movement of the motor, each valve disc is turned after half a revolution of the rotary disc rotated step by step by 900.

This opens the outlet ports and inlet ports through the opening released one after the other in the valve disc or through the non-perforated Quadrant of the valve disc closed.

If assumed as the starting position of a valve disc, for example is that the opening in the valve disc is straight with the outlet opening (81) covers a chamber, then this disc moves after every half revolution of the rotating disc the following Curtains off: after the 1st half turn starts for the chamber of ksauetakt. The Vontile disk is rotated by 900 at the beginning of the bar been. As a result, the opening in the valve disc is connected to the suction opening (80) the Chamber has been brought to cover. At the same time the outlet opening was through closed the unbroken part of the Vontile disc.

After the 2nd half turn, the Vontile disc is turned by the four-way turn the suction opening is also closed, and the compression cycle begins for the chamber under consideration.

After the third half turn of the rotating disk and The quarter turn of the valve disc, coupled with it, leaves the inlet and outlet openings locked, the ignition cycle begins.

After the 4th half turn there is the opening in the valve disc again with the outlet opening (81) to cover, the exhaust stroke begins and the The process is repeated overall.

The gradual rotation of the valve disks about their axes in the As in embodiment 1, the rotary disk is secured by cams (83) on the valve disks achieved. These cams engage when the rotating disk rotates together with the recessed valve disks around the motor axis in corresponding cams (84), the are incorporated in the motor casing at rest; they cause the valve disc to rotate 90 ° relative to the rotating disc.

There is a 90 ° turn after every half turn of the rotary disk must take place, 4 cams are evenly distributed on the circumference of the valve disks attached and on the circumference of the engine casing 2 at an angular distance of 1800. During the engagement of the cam on the valve disc and in the motor casing rotates - the rotary disk moves about a distance of 300 - 400 further.

The 4-valve discs for the 4 chambers are built in exactly the same way, they have the same shape and the same distribution of the Cam on the disc circumference. Regarding the suction opening (resp.

the outlet opening) the valve disks, one at a time rotated by 90 ° against each other, inserted into the recesses in the rotating disc. With this arrangement, each disc performs the same control processes for the and outlet openings of the individual chambers, but from Xan-er to chamber offset by the time that corresponds to half a revolution of the rotary disk. on In this way, the respective inlet and outlet openings are in the correct position for all chambers Moment released or locked.

Since all valve disks always have the same orientation relative to one another retained, valve discs can be coupled to one another; for example In the arrangement according to FIG. 2.6, the valve disks can be rotated about the same axis (82) (78) and (781) are rigidly connected to one another by a common axis4 Man achieved by the fact that only one disc from the outside in incremental rotary motion Must be relocated, or that the cam of a disc necessary for control can be distributed to the disks coupled to one another.

To seal the working chambers against the valve disks are in the Circumferential washer fitted around the inlet and outlet openings with sealing rings (85), which press against the valve discs.

With this arrangement of the inlet and outlet bores and the valve disks The following advantages result in the rotating disk: With one chamber the suction and discharge of the working gas is carried out by means of a c h i e d An opening in the chamber wall, the control of the suction process and the ejection process takes place through an opening in a disc.

Only 4 valve slices are therefore required for a 4-chamber engine, in the Compared to the 8 otherwise normally necessary Vontiles. As the expulsion of the consumed Gas through the same opening in the valve disc as the suction takes place, is also in this embodiment the wall of the opening in the valve disc directly after the exhaust stroke through the cold gases during intake, as in the previous one Embodiment 1, always cooled again. A "burning" of the material, as is often the case This avoids observing the usual exhaust valves. As with the Embodiment 1 uses the valve disks to avoid increased friction by the compression and expansion pressure on the discs, only at the beginning or Rotated at the end of the measure.

ß @ The supply and discharge of the working gas to the inlet and outlet openings the chambers takes place through the rotating disk. The channels for guiding the Working gas lie within the disk, advantageously in a spiral curved Course.

The course of these channels is shown in dashed lines in FIGS. 2.5 and 2.7. With the assumed direction of rotation of the rotating disk clockwise, the unused Working gas through the two boreholes (80), (80 ') and channels (73), (73') all 4 Arbeitslcammorn fed and through the two bores (81), (81 ') and channels (74), (74 ') the used working gas is led away from all 4 chambers again, Due to the spiral arrangement of the inlet and outlet channels, when filling the working chambers with working gas and when diverting the used working gas a high degree of efficiency achieved.

These spirally formed channels act when the rotating disk rotates like "wind tunnels". This opens the inlet channel in the direction of rotation the rotary disk has an increased pressure generated in the outlet channel with an opening In the opposite direction of the rotary movement, a distributed pressure due to the suction effect. Pressure and suction therefore improve the degree of filling or

don degree of emptying with open inlet or outlet openings.

When controlling the inlet and outlet processes with valve disks According to Fig. 2.6 and 2.7, the selected arrangement of the holes in the rotary disc and the hole in the valve washers improves the filling effect even more. In the transition from the exhaust stroke to the intake stroke ubordoclct dio drilling in the Vontilschoibe for a moment at the same time a certain area in the suction opening (80) and in the outlet opening (81). During this phase there is a continuous one Connection from the inlet channel (73) via the inlet opening (80) to the chamber and through the outlet opening (81) towards the outlet channel (74). Due to the wind tunnel effect the spirally arranged inlet and outlet channels is unused during this period Working gas blown through the chamber and the remainder still remaining in the chamber used working gas is removed from the chamber in a flushing process., The same Rinsing effects can also be used when controlling the suction and discharge process with the usual Valves achieve when the channels in the rotary disc, as indicated in Fig.2.5, are mapped spirally and the opening and closing times of the valves has been adjusted so that the inlet and outlet valve during a small period of time are open at the same time, the wind tunnel effect and thus the suction and pressure effect weh-.

rend of the exhaust and intake stroke, and the flushing effect during the transition phase from exhaust to intake stroke increase with increasing engine speed.

The channels are designed in the area of the edge of the rotating disc so that that the openings (86) of the inlet channels are directed to one side of the rotary disk are (for example as in Fig.2.7 towards the top of the. Disk), and the openings (87) of the outlet channels to the other side (in Fig. 2.7 to the underside of the disc there). This results in a spatially separate supply and discharge of the working gas to or from the channel openings in the rotary disk. In the area that sweep over these openings of the channels when rotating the rotating disk, is in Motor casing above and below the rotating pulley, one ring-shaped channel each attached. One of these annular channels is in spatial connection with the carburetor system and serves to supply the working gas to the inlet channels in the rotary disk down, the other ring-shaped channel receives the used gases and conducts them into the exhaust system.

The spark plugs for igniting the combustion gas are in holes housed in the rotating disk (88). Through corresponding recesses in the The rotating discs are the ignition electrodes of the individual spark plugs with the respective one Spatially connected work chambers. The easiest way to supply the high voltage is to use it through spark gaps or sliding contact gaps in the fixed motor housing are attached at suitable intervals. By advancing all spark gaps in the direction of or in the opposite direction of the rotational direction of the rotary disc can Ignition timing can be varied.

All elements attached to the rotating disk to control the Motor processes are arranged axially symmetrically with respect to the axis of rotation of the rotary disk. This ensures that the rotating pulley is synchronized.

In the embodiment according to FIG. 3.1 of the motor according to the invention the cylindrical intermediate pieces (55) are firmly connected to the partition, partition and cylinder pieces form a unit. This has the advantage that the Sealing strips between the flat surfaces of the cylindrical spacers and the partition, (63) in Fig. 2.3 are omitted.

In this embodiment, the partition (22) stirs during the sequence of movements around the axis (o) no pure rotary movement as in Fig. 2.3. The movement the partition consists of a rotary movement around the axis (o). and one Rotary pendulum movement around the axis (89) which is perpendicular to the partition. For storage the partition in the motor housing (11) are at the piercing points of the axis (o) through the GnhSuscwand bolts (90) attached so that they go into the interior of the spherical surface protrude. These protruding Dolzenenden engage in corresponding grooves (91), the in the convex spherical (sliding on the inner spherical surface) 'surfaces (2 ') of the partition (22) are incorporated. The rotation of the partition around the axis (o) is carried out in this way by a rotation around the bolts, and the rotary pendulum motion around the axis (89) by sliding the groove along the bolt.

The bolt probes protruding into the engine compartment can be conical the grooves in the convex spherical surface of the partition wall accordingly with a wedge-shaped profile.

By slightly screwing the bolts further into the engine compartment into it, you can then easily readjust this bearing.

The generated rotary movement of the motor is in this AusfUhrungsform picked up by a toothed ring that is attached to the outer surface of the UX running disk is. This gear ring can also be used to start the engine.

To the exerted on the partition wall (22) during the expansion of the working gas To transfer rotational forces "cleanly" to the rotating disk without the sealing surfaces The load between the cylindrical spacer and the rotating disc is a partition and The rotating disk is rotatably connected to one another by bolts (92).

A particularly advantageous variant of embodiment 2 of the invention Motor is shown in Fig. 3.2.

This embodiment combines the advantages of construction 3.1 with those of the embodiment according to 2.1-2.7. As sketched in Fig. 3.2, are the cylindrical intermediate pieces are not firmly connected to the partition (22), but each form a unit with a circular disk (22 '). Between these two circular discs is the partition (22), the circular disks with the permanently attached cylindrical Intermediate pieces slide, rotatable about the bolt (56), on the partition. At this Construction, the partition wall performs a pure rotary movement around the axis (o); she can therefore with a ball or roller bearing lying around the shaft as in the Embodiment 2.1-2.7 are rotatably mounted in the motor housing. On the other hand remains the advantage of the construction according to 3.1 is retained: the cylindrical surfaces on the flat surfaces Seals (63) lying between pieces in embodiment 2 / are not necessary the rigid connection of the cylindrical intermediate pieces with the rice disks (22 '). - The rotary movement is picked up on the shaft around the axis (0).

The seals located in embodiment 2 in the partition wall (61) for sealing the chamber against the concave spherical surface are in the present case Embodiment housed in the surfaces (2 ') around the circumference of the circular disks. Since the expansion pressure after the ignition of the working gas of the between. the circle disks lying partition (22) is added, it is not necessary to do this To make disks particularly stable. The thickness of the circular disks is only that great chosen that the sealing rings in the area around the circumference sufficient Find space.

All design features of embodiment 2, wio z.D. the advantageous Formation of the inclined half-disks into only one pure rotational movement executing rotary disc, the advantageous arrangement of all inlet and outlet openings, -vontila, -channels in the rotating disk and the resulting o simple Controllability of the valves or valve discs, the wind tunnel effect and the flushing effect remain in this embodiment.

The motor housing with the concave spherical surface is made from 2 halves formed. The parting plane runs in the central plane (66 ', Fig. 2.3) of the Revolving disk, so that - with advantage for technical production - 2 each other completely the same half-tone with a hemispherical surface for the top two or lower chambers are formed. These two halves are used in Beroich screwed together outside the rotating disc. A seal, in the manner of a head clearing of a piston engine, between the two halves of the engine housing is unnecessary, because the resilient sealing rings (60, Fig. 2.3), which the motor housing and the rotating disk, against each other Dichton, take on this task. The assembly and disassembly of the invention Motors is therefore very easy to implement. It is because of the ease of manufacture Advantageous, even if the rotating disk is divided into two halves with respect to the center plane is trained.

Figures 1.1-3.2 give examples of possible embodiments of motors or pumps with working chambers designed according to the invention. These engines address the shortcomings and disadvantages of conventional engines avoided. A Motor with working chambers designed according to the invention is distinguished by its significant advantages compared to motors of known design: The structure of the motor according to the invention is very simple, it consists of only a few, easy to assemble and disassemble individual parts, which are also due to because symmetrical constructions are partly equal to each other. This results in advantages such as material savings, low manufacturing, maintenance and spare parts costs.

The rotational movement of the motor according to the invention is d i r e k t by creates the pressure of the expanding gases on the rotatable partition. In the making no additional eccentrics, shafts or gears are involved in the rotary movement. All embodiments of the engine according to the invention are therefore devoid of any Eccentric movement, the embodiment 1 is practically free from reciprocating movements Embodiments 2 and 3.2 show only a very slight to and fro movement (of the cylindrical spacers). As a result, great smoothness is achieved and the wear and tear of important engine parts is greatly reduced. The low wear the operational safety benefits and allows a long service life of these engines expect.

The constructions of the invention indicated in the exemplary embodiments Motors are designed so that all essential bearings are in the form of adjustable Roll or slide bearings are formed. This also ensures a long service life achieved.

Since the movement processes that occur in the engine according to the invention, are essentially only rotary movements, versions with very high numbers of revolutions should be used to be possible.

In the execution forms according to Fig. 2.3, 3.1 and 3.2 the seals are designed so that the surfaces to be sealed against each other in the abzudichtondon Always slide areas with mutually parallel surfaces on top of each other. Dio in one of the two surfaces to be sealed against each other, incorporated sealing strips or rings therefore always press vertically (or always in the same direction) the respective other surface to be sealed, in the same way as the sealing rings in the piston engine. The sealing problems of the rotary engine and orbital engine occur in the engine according to the invention does not occur.

The concept of the engine according to the invention allows all Elemonto, which are necessary to control the movement sequence - inlet valves, outlet valves, Spark plugs - to be housed in rotating chamber walls. So you can do it Take advantage of existing movement to control the processes.

The valve disks provided in the rotating disks are open in this way via a very simple mechanism, without detours via rocker arms or camshafts or the like, to be controlled directly by cams mounted in the motor housing. the Movement of the valve disks is such that the disks only at the beginning of a cycle are rotated, while the cycle is running, the valve disks stand still. Due to the increased pressure on the discs during compression and expansion therefore, no friction is generated. All inlet and outlet processes are controlled over a total of only 4 valve slices; the discs are designed so that for everyone Chambers discs of the same design are used. As the expulsion and suction of the working gas for a chamber through the same opening in a valve disc takes place, is avoided by the constantly repeated grooving during the suction process, that parts of the valve disk, as can be observed with conventional valves, overheated will and burn.

When using conventional valves, built into a rotating chamber wall of the engine according to the invention, new advantages are achieved for these valves: the valves are closed with a speed-dependent restoring force.

The installed in the rotary disc of the embodiment 2 and 3, Inlet and outlet channels formed in a spiral shape supporton through their wind tunnel effect the intake and exhaust process.

The specified embodiment of the valve disks themselves also contributes to an improved filling of the chambers with working gas through a flushing process in the transition phase from exhausting to intake.

The movement of the dividing wall and half-discs or rotating disc takes place so that the increase in volume of a chamber is coupled with the equally large decrease in volume the adjacent chamber without changing the total volume. The spherical shape of the engine compartment in embodiments 2 and 3 also brings in comparison to all other conceivable geometries with the best possible volume utilization. The motors formed according to the invention are therefore very compact, even with large-volume working chambers. A 4-chamber motor according to the specified embodiments, for example with the volume of a chamber of 375 cm3, corresponding to a 4-cylinder piston engine with 1.3 liter displacement, has a radius of the inner sphere of approx. 7.5 cm. A spherical engine compartment with a radius of approx. 8 cm corresponds to a 2-liter piston engine. a 6-liter piston engine has a spherical radius of only approx. 12 cm.

L e r s e i t e

Claims (35)

PATENT CLAIMS 1. Motor for generating a rotary motion from the Increase in volume of a closed working chamber while expanding an enclosed one Working medium, e.g. 13. a combustion gas, or a pump to generate a suction odor pressure effect through volume change of a completed work skammer, thereby characterized in that an arboits chamber is formed by the space between each other "penetrating" areas or partial areas of at least one area with rotational symmetry (i), at least one surface (2) rotatably arranged about the axis of symmetry (o) and at least one further axis which is inclined about elne to the axis of symmetry (13) rotatably arranged surface (4), which when rotated about the axis of symmetry rotatable wall is also set in rotation by the action of this wall, wherein the "penetrations" of the surfaces are technically realized by the boundaries one surface slide on the other surface and / or a surface in recesses receding in the other area. 2. Motor or pump according to claim 1, characterized in that several chambers are bounded by the same rotationally symmetrical surface, wherein the chambers migrate in the course of the movement relative to the rotationally symmetrical surface and several chambers one after the other di the same areas of the surface of the rotationally symmetrical Can paint over the surface. 3. Motor or pump according to claim 1-2, characterized in that the surfaces and "penetrations" mentioned in claim 1 are formed as follows are: the surface with rotational symmetry due to the concave surface a vertical rotating cylinder, the rotatable around the axis of rotation arranged (n) Areas through the flat surface () of a or moor lying parallel to the axis Discs ("partition") and placed on the face (s) of this disc (n) Ice disks ("cover disks"), the inclined to the axis of rotation (n) Areas through the surface (s) of one or more semicircular disks ("Half-disks"), the partition wall rotatably arranged around the axis of rotation with convex cylindrical edge surfaces (2 ') in the concave cylindrical surface (1) slides, along with the half-disk (s) (44) arranged inclined to the axis of rotation their semi-circular edge area (s) in one or more planes, to the cylinder axis Slip inclined groove (6) machined into the cylinder wall ("housing wall") and with their straight edge area (s) (4 ') on the plane Slide surface (s) (2) of the partition wall (22) rotatable about the cylinder axis. 4. Motor or pump according to claim 1-2, characterized in that the surfaces and "penetrations" mentioned in claim 1 are formed as follows are: the surface with rotational symmetry through the concave surface of a sphere, the surface (s) rotatably arranged around the axis of rotation through the flat surface (s) one or more disk (s) lying parallel to the axis ("partition wall") which are used for Axis of rotation inclined surfaces through the surface (s) of a or more semicircular disk (s) ("half disks"), the one around the axis of rotation rotatably arranged partition with convex spherical edge surfaces (2 ') in the concave spherical surface slides, the inclined to the axis of rotation (nl Halbschoibefn) (44) with their semi-circular edge area (s) in one or more flat, inclined to the axis, worked into the spherical wall (housing wall ") Groove (6) slide, and with their straight edge area (s) (4 ') slide on the flat surface (s) (2) of the partition wall (22) rotatable about the axis. 5. Motor or pump according to claim 4, characterized by at least an intermediate piece (55) with a flat surface, a convex cylindrical jacket surface and 2 convex spherical end faces, the flat face on one of the flat surfaces of the partition, which is rotatably arranged around the axis, slides, on the convex cylindrical surface, which is correspondingly concave cylindrical formed edge surface of the inclined disk (s) slides and the Convex spherical end faces slide on the concave spherical surface. 6.. Motor or pump according to claim 5, characterized in that the cylindrical intermediate piece (s) with the (the) around the axis of the assembly rotatable partition is rigidly connected. 7. Motor or pump according to claim 5, characterized in that the (the) cylindrical) intermediate piece (s) each rigidly connected to a disk (22 ') is (are) sliding on the partition (22) rotatable about the axis of the assembly (slide). 8. Motor according to claim 3-7, characterized in that the through the arrangement according to the invention given change in volume of the individual chambers of the 4-caniner version with it is exploited, the engine as a 4-stroke engine to operate. 9. Motor or pump according to claim 3 - 8, characterized gelcennzeichnct, that on both sides of the partition wall 2 half-disks slide in the groove (s), their wheels Jo sliding on the partition wall formed into a cutting edge (14) are whose bevel is attached to the side of the half-disks facing away from the chamber are. 10. Motor or pump according to claim 3 - 9, characterized nekennzeichnot, that the centrifugal forces of the half disks that arise during operation are caused by counterweights (21) are partially, completely or over compensated. 11. Motor or pump according to claim 10, characterized by a speed dependent compensation. 12. Motor or pump according to claim 5 - 9, characterized in that that the half-disks sliding in the groove (s) on one side of the partition with which on the other side of the partition wall are rigidly connected or form a unit ("rotary disk") (66). 13. Motor or pump according to claim 3 - 12, characterized in that that for guiding the half-disk (s) or the rotating disk instead of in the housing wall incorporated groove (s), ball or roller bearings mounted in the housing wall to serve. 14. Motor or pump according to claim 13, characterized in that the rollers of the roller bearings used for guidance can be rotated about bolts on a free movable ring (69) are arranged, the rollers having conical running surfaces and can be moved onto the bolt by means of an adjustment device. 15. Motor or pump according to claim 1 - 14, thereby connected, that the compression ratio is determined by the angle of inclination (16) dor inclined discs against the axis of rotation and / or by dio Diclce the inner chamber walls and / or odor enclosed by the surface with rotational symmetry by filling in dead space in the arboits chamber. 16. Motor odor pump according to claim 4-15, characterized in that that arbitrarily high compression ratios achieved by filling in dead space been. 17. Motor or pump according to claim 1-16, characterized by channels and cavities (36, 37) in the rotating engine or pump parts so arranged are that gases and / or liquids for cooling and / or lubrication due to the centrifugal force acting on it through the rotating motor or pump parts will. 18. Motor according to claim 1 - 17, characterized in that the input and exhaust processes are controlled by conventional valves and that the valves in rotating chamber walls in a radial direction or in a direction with a radial Component are arranged. 19. Motor according to claim 1S, characterized in that the valves can be controlled by cams attached to bodies of revolution, the bodies of revolution in turn by nocci distributed over the circumference, which are in corresponding cams reach into stationary parts of the housing, be rotated. 20. Motor or pump according to claim 1-17, characterized in that that the inlet and outlet openings of the chambers through one or several Schiobor with one or more openings opened or closed by The slide during the course of movement has its bearings relative to the chamber openings change and release or through their opening (on) the inlet and outlet openings close their unbroken parts. 21. Motor or pump according to claim 20, characterized in that identically designed for opening and closing all inlet openings and / or outlet openings Slider can be used. 22. Motor or pump according to claim 20-21, characterized in that that the inlet opening and the outlet opening of a chamber through a slide with an opening opened or is closed. 23. Motor according to claim 20-22, characterized in that the (the) Slider is moved at the beginning or at the end of a measure (are), whereby achieved is that due to the increased pressure during the compression and the work cycle no friction is exerted on the slide (s). 24. Motor or pump according to claim 20-23, characterized in that that the slide are designed as a body of revolution with one or more openings in the surface of rotation ("valve disks"), preferably flat disks with a or several through holes that rotate around their axes of rotation and through their openings open the channels for the supply and removal of the working mode or close by the uninterrupted parts. 25. Motor or pump according to claim 20-24, characterized in that that several slides are coupled to one another, whereby it is achieved that not Each valve disc must be controlled individually for itself. 26. Motor or pump according to claim 1 - 25, characterized in that that the inlet openings and / or outlet openings are located in rotating chamber walls. 27. Motor or pump according to claim 26, characterized in that the suction and discharge of a chamber takes place through one and the same opening, and that the predetermined rotation of the chamber wall is used to suck the and the working medium to be expelled in spatially separated channels the opening in the chamber wall or from the opening in the chamber wall (52 or 52 '). 28. Motor or pump according to claim 26, characterized in that the valves or slide for controlling the inlet and outlet processes in rotating Chamber walls are attached, whereby it is achieved that the predetermined rotational movement can be used to control the processes. 29. Motor or pump according to claim 28, characterized in that the valve disks are provided with cams distributed over their circumference, with corresponding cams come into engagement, which are in stationary housing parts are attached, thereby causing the valve discs to rotate. 30. Motor or pump according to claim 1 - 29 characterized in that the working medium through - preferably spirally curved - channels (73, 74) which mounted in rotating engine parts to and from the intake ports is directed away from the outlet openings. 31. Engine according to claim 30, characterized in that the inlet and the outlet openings of the chambers during the Transition from the exhaust cycle are fully or partially open at the same time as the intake cycle. 32. Motor or pump according to claim 1 - 31, characterized in that that the motor or pump housing is identical to 2, to the center plane (66 ') that to the axis of rotation inclined surface (s) is formed point-symmetrical eleventh. 33. Motor according to claim 1-32, characterized in that when used of a combustion gas, the ignition electrodes lie in rotating chamber walls. 34, engine according to claim 33, characterized in that the ignition voltage is supplied via radio links or spatially limited loop contact paths. 35. Engine according to claim 34, characterized in that the ignition point by moving the one in the stationary and / or the one in the rotating motor part Electrodes of the spark gaps or loop contact paths in the direction or in the opposite direction the rotary movement is set.