DE2117884A1 - ROTATING MOTOR - Google Patents

Description

Rotary Motor The invention relates generally to rotary motors and in particular rotary motors in a version with two rotors which are used for Execution of an oscillating rotation are supported against each other and lamellae or pistons wear, which are in an annular chamber when rotating the respective rotors move.

The lamellae of one rotor alternately move onto the lamellae of the other rotor to and from them to create a suction, a pressure, a working and to generate a discharge stroke. Such engines are in an article under the Headed "Rotary Shgines" by Riallace Chinitz in Scientific American, February 1969, and in an article entitled "Rotary Combustion Engines '"by R.F. Ansdale in Automobile Engineer, December 1962. Oscillating rotor motors have not yet found acceptance in practice, mainly as a result the inability to overcome the problems of excessive shock loads associated with occur with the oscillatory rotation of the rotors, and as a pole of difficulties in production. such engines. E "in engine in such a version, the has already been proposed, consists of an annular stator with a Water cooling jacket provided with suction and discharge openings o A drive shaft is rotatably mounted in the stator, and two rotors, the two lamellas resp.

Pistons included are designed to oscillate against each other stored on the drive shaft. Cams on the drive shaft work with the rotors together to alternately drive and anchor the rotors opposite the stator.

Large impact loads arise as a result of the alternating acceleration and decelerating the rotors from a rest position large amounts of energy are caused by the abrupt starting and stopping of the rotors is consumed.

In other recently proposed arrangements, energy hydraulically transmitted from the vibrating lamellar rotors to the drive shaft. In one such proposed arrangement, the engine has an annular chamber, through an outer jacket and adjacent ring parts educated which are provided on two vane rotors.

The rotor has four power lamellas or pistons and a hydraulic oil chamber is located between the adjacent rings of the rotor and the shaft of the motor. The power blades of the respective rotors work together to make expandable and contractible Form gas chambers in the annular chamber. The motor shaft is with a symmetrical one Provide the impeller with cams, which are located inside the hydraulic chamber. The rotors each carry a hydraulic lamella or a hydraulic piston, which or which is located in the oil chamber. The hydraulic pistons are on opposite sides Sides of the cams of the impeller. While the rotors are made to go through the explosion of fuel in the gas chambers to vibrate against each other, the respective hydraulic lamellae vibrate within the hydraulic oil chamber and act upon it the cams of the impeller alternate in order to set the drive shaft in rotation.

In another proposed motor of this type in which the power hydraulically transmitted to the drive shaft of the engine is an oil chamber provided within a ring which is arranged concentrically to the rotors of the motor is. The respective rotor is mechanically connected to a flywheel. The flywheel in turn is connected to the drive shaft via a drive spring. The respective rotor includes two hydraulic slats that are free on the drive shaft are rotatable. The hydraulic lamellae each carry slide valves with a backlash movement such that with the acceleration and deceleration of the hydraulic lamellae as a result the oscillation of the rotors against each other the slide valves alternately between trailing and leading positions in relation to their respective oil or

Hydraulic slats move back and forth as a result of the torque. During a power stroke of one of the rotors, the associated oil lamella is aligned with openings in the wall of the oil chamber, so that oil from one side to the other of the oil lamella can migrate through openings controlled by the lost motion valve. In a In the position of the valves, the oil lamellas are hydraulically interlocked in such a way that that both rotors travel at the same speed. After the common Movement through a certain angular path allows medium from one side to the hydraulic lamellae flow to the other to allow the rotors to swing against each other.

Extreme difficulties have been encountered with all engines of this type to successfully eliminate the shock loads caused by the standing / walking movement of the Rotors are generated, and thereby the motor shaft is given a jerk movement.

The known rotors of this type can only operate at extremely low speeds work. Hence the inability to jinit dee beach has acceleration and deceleration powers perfect cope with the vibration of the rotors the practical use of this type of rotary motor largely limited, so that they offer no advantages over reciprocating engines.

The invention is therefore based on the object of a rotary motor to create in a version with oscillating rotor, in which the rotors with a smooth motion swing that the acceleration forces as a result of the oscillation which brings rotors within acceptable limits.

Another object of the invention is to provide a rotary motor in oscillating rotary design, in which the rotors with a substantially sinusoidal Vibrate movement that greatly reduces and smooths the acceleration forces, caused by the vibration of the rotors.

The invention further aims to provide a rotary motor in vibrating rotor design, which has a self-contained hydraulic drive system which significantly reduces the number of moving mechanical parts that normally associated with this type of motor, and what the moment of inertia the lamellar rotor assemblies are significantly reduced, thus reducing the forces of inertia to reduce.

Another object of the invention is to provide a rotary motor in a swing rotor design with a shaft with two rotors, each for Rotation of the shaft opposite to each other and for oscillating rotation against each other, wherein drive means are provided which comprise at least one drive part, that in response to the oscillatory rotation of the rotors against each other Hubbewgbar and is rotatable about the axis of the drive shaft during its lifting movement, and wherein Means are provided which respond to the lifting movement of the drive part, such as that a rotation of the shaft and a movement of the drive part executing a lifting movement in a sinusoidal path around the axis of the shaft.

Another object of the invention is to provide a rotary motor in oscillating rotor design, with two vane rotors each for rotation opposite one another the drive shaft of the motor and for oscillating rotation are supported against each other, wherein hydraulically driven drive means are provided, the drive parts include, which are reciprocally movable in response to the oscillation of the rotors, wherein a reaction part in engagement with the drive parts executing a lifting movement can be brought and responded to, such that the drive shaft is set in rotation and that the drive parts executing a lifting movement have a sinusoidal shape Traversing the way around the axis of the shaft, with the rotors using hydraulically perform a lifting movement Drive parts are connected, so that they vibrate against each other in a steady sine waveform.

Another object of the invention is to provide a rotary motor with means that form a hydraulic circuit, with a chamber for hydraulic fluid is turned on in the circle, one in response to the flow of liquid in the chamber in the hydraulic circuit and out of the chamber rotatable shafts are provided are, two rotors each for rotating the shaft opposite and for oscillating rotation are mounted against each other and means are available which act on the oscillating rotation of the rotors respond to each other in such a way that a flow of hydraulic fluid into and out of the chamber to cause rotation of the shaft will.

Another object of the invention is to provide a rotary motor in N pulsating 11 version with a self-contained hydraulic circuit a chamber for hydraulic fluid, which is connected to the circuit, with two Rotors, each designed to rotate the shaft opposite one another and oscillate against one another are mounted in such a way that a flow of hydraulic fluid into the chamber and is effected from the chamber, and with drive means in response to the Flow of hydraulic fluid into and out of the chamber will take effect such that the Motor shaft is set in rotation and at the same time the rotors are hydraulically made to move in a steady sine wave to swing against each other.

Another object of the invention is to create a rotary motor, in which a combustion of fuel can take place in an outer chamber, which is separated from the engine parts during combustion, so that noise and load on the engine parts is prolonged, with the ignition occurring continuously, such that pollution problems are reduced, those from ignition The resulting high-pressure gases are fed to the engine parts after ignition.

For this purpose, a motor with two rotors can be provided according to the invention each having an identical set of gas fins or pistons, which vibrate relative to each other in an annular gas space. The slats of one The rotor oscillates relative to the lamellae of the other rotor, one after the other To form suction, compression, ignition and discharge strokes. The gas fins of the respective rotor extend radially outward from one Bearing ring in a sliding and sealing abutment on the inner surface of an annular Water jacket that covers the stationary outer wall of the motor housing or the stator section forms.

Extending radially from the bearing ring of the respective rotor after inside oil lamellae or hydraulic lamellae, each having a radial extension or Form continuation of a corresponding gas lamella. The respective rotor is open the drive shaft to rotate the drive shaft opposite and against each other around the Axis of the drive shaft stored around. For example, the inner ones extend Peripherals of the hydraulic lamellae in a sliding and sealing system to the outer periphery of the drive shaft of the motor, rotatable about the respective rotors to be stored on the drive shaft.

Alternatively, the inner ends of the hydraulic lamellae with inner Ring parts be connected, which in turn rotatably mounted on the drive shaft are. The two rotors are mounted on the drive shaft so that their ring parts End to end together between two axially spaced apart annular End wall parts lie. The end wall parts can be arranged by two axially spaced Flywheels be formed, which are each firmly connected to the drive shaft. The respective gas lamella and the respective hydraulic lamella extend over the entire axial distance between the end wall parts and is in one sliding and sealing system on it.

Two gas louvres sitting next to each other and two next to each other Seated hydraulic lamellae together form the moving parts of an expandable Gas chamber or an expandable hydraulic chamber. The gas chambers are through each formed two gas lamellae sitting next to each other, whereby a slat each belongs to a rotor and the lamellae each with the outer surfaces of the Rings, the inner wall of the water jacket and the axially spaced end wall parts cooperate by the two flywheels or by fixed hollow end wall parts can be formed that protrude from the water jacket inward. The hydraulic chambers are each formed by two hydraulic lamellae sitting next to each other, whereby one lamella each belongs to a rotor and the lamellae each with the inner surfaces the rings, the outer surface of the drive shaft and the two flywheels or others Cooperate end wall parts which are attached to the shaft.

The respective flywheel carries a number of radial cylinders, and the respective cylinder on the respective flywheel is hydraulically connected to one of the Hydraulic chambers in connection. A ball piston can be lifted in the respective cylinder arranged such that it has a radial stroke movement relative to the axis of the drive shaft can perform. The spherical pistons grip the inner surface or path of a cam guide on, which has such a shape that with the push of a spherical piston radially afterwards outside the cylinder opposite the piston on the surface of the cam guide with a Force acts, which has a tangential component, which over the wall of the cylinder, in which the piston sits is so effective that the flywheels are made to about the axis of the drive shaft of the curve guide opposite æu turn Un with it the drive shaft rotates transferred to. The shape of the Cam surface is provided so that the respective spherical piston in a sine wave form or migrates in a wave path around the axis of the drive shaft. The term II sinusoidal path tt means that the spherical piston is between two extreme points wander back and forth while rotating about the axis of the drive shaft, and that the position of the respective spherical piston in the longitudinal direction of its stroke is a sine function is the angular position of the spherical piston relative to the axis of the drive shaft.

When two hydraulic lamellae are sitting next to each other in the direction of each other migrate, they push oil into two cylinders that are assigned to one another and into the opposite one Flywheels so that the balls in the two cylinders oppose radially outwards the curve surface can be pressed. On both sides are the hydraulic chambers at the same time enlarged, because of the separation of the lamellas, the expandable ones Form walls to allow oil to flow back out of the cylinders, with which the chambers are connected to a retraction of the respective spherical piston to enable.

The cylinders and the balls are opposite the ramp surfaces and the hydraulic chambers oriented so that when one of the pistons is acted upon by oil pressure is pushed radially outward before its movement from a point on the ramp has started, which lies radially inwardly of the shaft, and a movement towards one Executes point on the ramp that is furthest outside the shaft opposite. The pistons on both sides it can retract while moving towards a point on the ramp migrate, which is located radially inward towards the axis of the shaft. With when a piston moves outwards, the pistons next to it move in corresponding measure back, and the volume remains constant.

In one embodiment of the invention, the respective rotor Equipped with four gas lamellae and four hydraulic lamellae. Form the gas lamellae So eight gas chambers in the ring-shaped gas space or two sets of four gas chambers each, of which one set expands while the other set contracts accordingly, while the rotors swing against each other. Two ignition devices are available with the annular gas space at diametrically opposite points or at top dead center and in connection at bottom dead center. At the end of a swing stroke of the rotors in which the lamellas come closest to each other to fully contract a set of chambers and to fully expand the other set of gas chambers stands one of the contracted ones Gas chambers in communication with one of the ignition devices, and one diametrically opposite contracted gas chamber is in communication with the other ignition device.

The two sets of gas chambers alternately expand and pull together while moving around the axis of the motor shaft to the stator part of the motor rotate opposite. The respective gas chamber and the associated hydraulic chamber are contracted when it or its radial center line is at one or the other ignition device or a point located 900 to the respective ignition device is offset.

Two suction openings are attached to the outer wall of the motor housing Molded in diametrically opposite points.

The leading end of the respective suction openings is located about 900 offset from one of the ignition devices.

Correspondingly, diametrically on the outer wall of the motor housing opposite points in deg uadrants that adjoin the suction openings, two outlet openings are provided, such that the respective ignition device essentially at 900 opposite the leading end there was a suction opening in one next to it Quadrant and substantially 900 opposite the trailing end of an outlet opening is arranged, which is in the opposite, adjoining quadrant is located. The rotors rotate in such a direction that the respective chamber successively with an intake opening, an ignition device and an outlet opening communicates. When a collapsed chamber with a suction port communicating, it begins to expand and take a load of fuel through the suction opening. After moving completely apart the Chamber in the quadrant immediately in front of the ignition device moves the gas lamella, which forms the trailing wall of the chamber, in the direction of the gas lamella, which forms the leading wall to compress the fuel charge. When the chamber when it reaches its fully contracted state, it comes into contact with the Ignition device, and thereby the compressed fuel is ignited, so that the Chamber moves apart in one working stroke. With the opening of the chamber as a result of the ignition of the fuel, the leading gas lamella migrates Chamber at the leading end of the subsequent outlet opening past to the burned Allow fuel out of the annular space. The same situation lies at diametrically opposite points in the annular combustion chamber. The two Lamella sets thus work together to create two diametrically opposed working chambers, two diametrically opposed compression chambers and two diametrically opposed To form suction chambers, depending on their relative positions, the ignition devices and the Intake and outlet openings opposite.

The simultaneous ignition of the two ignition devices causes a Expansion of the gases in the diametrically opposite working chambers, and the one next to it seated compression and discharge chambers move together in a corresponding manner, while the suction chambers move apart with the working chambers.

While a gas chamber, which is formed between two gas lamellae, moves apart, moves the corresponding hydraulic chamber apart at the same time, to allow oil to flow out of the two cylinders with which it is in There is a connection in order to enable the piston to be retracted into this cylinder. Conversely, if two gas lamellae move towards each other, the corresponding ones move Hydraulic lamellae also move towards each other in order to press oil into the two cylinders, which are related to the corresponding pistons in these cylinders to press radially outwards against the surface of the respective approach guides. With the moving together and moving apart of the two sets of lamellas will be Oil pushed in and out of alternate cylinder sets to the flywheels to drive.

In another embodiment of the invention, two are external Combustion chambers at diametrically opposite top dead center and bottom dead center points arranged instead of normal ignition devices. The outer combustion chambers are off refractory material formed or lined with it. The outer combustion chambers are the cooling effects of the discharge, suction and compression strokes are not and cannot therefore reach very hot temperatures while the engine is running and on this Temperatures are maintained. The outer combustion chambers each have an inlet opening, the on one side of the dead center, as well as an outlet opening, which is on the other side of the dead center. If one of the converging Gas chambers approaches a dead center, it is with the inlet opening of the associated outer combustion chamber in communication to compressed air from the gas chamber through the Release inlet opening into the outer combustion chamber. The inlet port is then through the forward movement of the trailing lamella of the gas chamber closed while the gas chamber moves to the dead center position. While the gas chamber is in the dead center position is located, fuel is injected into the outer combustion chamber, and the mixture of fuel and compressed air or compressed gas is ignited while the gas chamber is in the dead center position and not in connection with the outer combustion chamber stands so that no fuel is introduced into the gas chamber, which is formed by the space between the slats. When the startled If the gas chamber moves slightly beyond the dead center position, it arrives at the outlet opening the outer combustion chamber in connection, and the white-hot, under high pressure Gases are returned to the collapsed gas chamber that is in the space between the side by side seated slats is formed in order to move the To effect gas chamber in one working stroke. If the outer combustion chamber is provided Violence of the explosion limited to the running noise and the outer chamber the burden of Reduce engine parts. Furthermore, the gases swirled and mixed with the fuel entering the outer combustion chamber is injected.

The rotors rotate continuously in the same direction while running Engine. There is no stopping and starting or counter-rotation of one or of the other rotor. An oscillation of the rotors against each other occurs as a result of the The fact that a rotor increases its angular velocity during the others reduced its angular velocity, either with every explosion or opposite any sequence of explosions in the gas space of the drive shaft.

The invention is described below on the basis of exemplary embodiments explained in more detail with reference to the drawings. In the drawings: Fig. 1 is an axial section of a rotary motor on the line 1-1 of FIGS. 3, 2 Section on the line 2-2 of FIG. 1, FIG. 5 is a section on the line 3-3 of FIG. 1, Fig. 4 is a section on the line 4-4 of Fig. 1, Fig. 5a to 5i are schematic representations showing the locations of certain parts of the engine according to FIG Representation in Fig. 1 to 4 in successive work phases, 6 is a graphical representation of the movement of certain parts of the engine according to FIG the representation in Fig. 1 to 4 during successive work phases, Fig. 7 shows a representation corresponding to FIG. 1 of a further exemplary embodiment of a rotary motor and FIG. 8 is a section on the line 8-8 of FIG. 7.

As shown in FIGS. 1 to 4, the invention consists in one Rotary motor with a shaft 2, two rotors 4 and 6, each for rotation the shaft 2 opposite and are mounted for oscillating rotation against each other, and with Drive means 8 and 9, which include drive parts lo and 1i, which in response perform a reciprocating motion against each other on an oscillatory rotation of the rotors 4 and 6 can. Means in the form of curved guides 12 and 13 are also provided, which respond to a stroke movement of the drive parts io or 11, so, that a rotation of the shaft 2 is caused. The cam guides 12 and 13 have endless run-up surfaces 14 and 15, which are connected to the respective drive parts 1o or i1 cooperate to set the shaft 2 in rotation when the drive parts perform a lifting movement.

If the drive part loa executes a lifting movement, for example, it acts on the ramp surface 14 in order to set the shaft 2 in rotation. These Shaft 2 is rotatably arranged opposite the drive part loa, such that with the turning of the shaft the drive part 1o is guided around the axis of the shaft, how this will be described in detail. The drive part 1oa leads a Stroke movement in the radial direction with respect to the axis of the shaft 2 during an oscillating rotation of the rotors 4 and 6 against each other, and the shape of the cam surface 14 is provided so that that it hears a movement of the drive part loa in a sinusoidal orbit, while it rotates with the shaft 2 around the axis of the shaft 2.

As shown in FIGS. 2 and 4, the cam guides 12 have and 13 are identical in shape and are in phase opposite to each other the axis of the shaft. The cam guide 12 is arranged with peripherally spaced Provided cams 16 which extend in the direction of the axis of the shaft 2 to curve parts 18 leading radially inward at the Curve surface 14 to form. It is also provided with curved portions extending radially outward 20 provided, which are attached to the radially inwardly extending portions 18 of the cams 16 connect so that the drive parts 1oa radially from the axis of the shaft 2 can be moved away while they are from a radially inwardly extending portion 18 migrate to an adjacent, radially outwardly extending portion 20, and that they can be retracted radially in the direction of the shaft 2 while they from a radially outwardly extending part 20 to the part 20 sitting next to it, migrate radially inwardly extending portion 16; while the drive parts 1oa each rotate around the axis of shaft 2.

Radially extending, end, open cylinders 22 and 23 are rotatably arranged opposite the shaft 2, and the drive parts 1o and 11 are made each of a piston, which is in the open end of the respective cylinder 22 or 23 seated. In the illustrated embodiment, there is the respective piston from a ball seated in the open end of the cylinder 22 and 23, respectively. For example the drive part loa consists of a spherical piston, which is in the open end of a Cylinder 22a sits and protrudes from it and is in contact with the cam surface 14 is located.

The illustrated embodiment of the invention comprises a hydraulic circuit with a chamber 25 for hydraulic fluid. The chamber 25 is switched into the hydraulic circuit. The cylinders 22 and 23 are in the hydraulic circuit switched on and are in a hydraulic connection with the chamber 25.

Referring particularly to Figure 3, the illustrated engine comprises Means 28a, Doa, which respond to an oscillatory rotation of the rotors 4 and 6 against each other, such that hydraulic fluid flows from the chamber 25 into the cylinder 22a to so that the piston can move up radially opposite the axis of the shaft 2, while the piston loa at the innermost point of an inwardly extending portion 18 of the curved surface 14 wanders past. The means 28a and 30a have the Porm of Hydraulic vanes that are movable away from each other to flow back to allow the hydraulic fluid from the cylinder 22a into the chamber 25 while the piston loa at the outermost point of an outwardly extending Part 20 of the cam surface 14 wanders past so that the piston loa radially of the axis the shaft 2 is withdrawn opposite, while it is farthest from the radial outward point in the direction of the following radially innermost Point of the curved surface 14 moves. The lamellae 28a and foa form the movable ones Walls of an expandable and collapsible chamber 52a in space 25, wherein there is a hydraulic connection with the cylinder 22a. The slats 28a and So foa are in the direction of each other and away from each other movable, in response to the oscillatory rotation of the rotors 4 and 6 to respectively cause hydraulic fluid to flow into cylinder 22a and piston loa is pushed radially outward, and the hydraulic fluid from the cylinder 22a flows into the chamber 32a when the piston loa moves radially inward.

The hydraulic lamellae 28a and 30a each sit on one of the rotors. The lamella 28a sits on the rotor 4 and the lamella noa sits on the rotor 6. The space 25 is annular and the shaft 2 extends axially through the space, such that the outer surface of the shaft 2 is the inner cylindrical wall of the annular space 25 forms. The rotors are each provided with a ring that has an inner diameter which is larger than the diameter of the shaft 2. The rotor 4 has a ring 54, and the rotor 6 has a ring 56. The rings 34 and 36 are relatively seated end to end to each other and concentric to the shaft 2, such that the inner surfaces of the rings 24 and 26 form the outer cylindrical wall of the space 25.

The space 25 is further defined by two axially spaced end wall parts 38 and 40 limited, (Fig. 1), the rotatably seated on the shaft 2 and radially from are led away from her.

The respective end wall part 58 or 40 is at the outer end of one of the Rings on to form an end wall of space 25.

The end wall portion 58 rests against the outer end of the ring 56, and the End wall portion 40 rests against the outer end of ring 34.

Ring seals 38b and 40b are seated in the end wall portions 38, respectively and 40. The end wall portions 38 and 40 are thus in sliding and sealing Abutment at the outer ends of the rings 54 and 36, respectively.

The hydraulic lamellae 28a and 30a each extend between the inner and outer cylindrical walls of the space 25, as well as between the end walls 38 and 40 of the space 25 to form an expandable and collapsible chamber 32a to form. The cylinder 22a is located in the end wall 38 and has an opening 42a in the end wall 38 together with a recess 44a in the shaft 2 provide a hydraulic connection between the chamber 32a and the cylinder 22. Corresponding the cylinder 23a sits in the end wall part 40 and is through an opening 43a in the part 40 is connected to the chamber 32a together with a recess 45a in the shaft 2.

As a result, the cylinders 22a and 23a, the chamber 32a, the openings act 42a and 43a and the recesses 44a and. 45a together to form a closed hydraulic system to form, in which the pistons loa and 11a movable walls of the closed hydraulic system and radially outward in response to the contraction of the chamber 32a are movable to * narrowly speaking the volume of the cylinders 22a and 23a enlarge. A subsequent expansion of the chamber 32a enables a radial expansion Retraction of pistons loa and 11a * in and a corresponding Reduction of the volume of the cylinders 22a and 2).

The motor shown has a housing or a stator part with a cylindrical water jacket having an outer cylindrical wall 48 and an inner cylindrical w-and 49, which are concentric to the blades 34 and 36 and to Axis of the shaft 2 are arranged. The cylindrical wall 49 forms an annular one Gas space 50 with the clamps 34 and 36, the outer surfaces of the rings 34 and 36 form the inner cylindrical wall of the annulus 50, while the inner surface of the cylindrical wall 49 forms the outer cylindrical wall of the annular space 50. The peripheral edges of the end wall pieces 58 and 4o extend in a sliding manner and sealing engagement with the inner surface of the cylindrical wall 49 of the water jacket, to form end walls for the annular gas space 50.

As shown in FIG. 3, two gas lamellae 52a extend and 54a away from rings 34 and 56, respectively, and they lead radially into a sliding one Rest on the inner surface of the cylindrical wall 49 of the water jacket. aside from that they extend axially between end wall portions 38 and 40 in a sliding manner Attachment to it. Drive in a way that will be described in detail later the gas lamellae 52a and 54a towards and away from one another, namely with respect to with the rotation of the rotors 4 and 6 around the axis of the elle 2 to produce a corresponding oscillating movement the hydraulic oil lamellae 28a and 3oa to cause the chamber 32a to alternate is collapsed and expanded. The gas fins 52a and 54a, the the oil lamellae 28a and 30a are assigned, cause the oil lamellae 28a and 30a alternately move the chamber 28a apart and move together, so that oil from the chamber 52a into the hydraulic cylinders 22a and 23a, which are assigned to the chamber 52a are pumped in or pumped out of them. With the closing of the chamber 32a, the associated pistons 1oa and 11a are radially against the surfaces 14 and 15 the curve guides 12 or 13 driven. Those exerted by pistons loa and 11a Forces against the corresponding piston surfaces 14 and 15 have a tangential component as a result of the shape of the curved surfaces. These impart tangential components the shaft 2 a rotary movement as a result of the abutment of the pistons 1oa and 11a to the Walls of the associated cylinders 22a and 23a.

In principle, therefore, the engine shown in FIGS. 1 to 4 comprises two gas lamellae 52a and 54a, which generate energy to move apart the associated hydraulic chamber 32a and to collapse. This moving apart and moving together of the chamber 32a causes an upward movement or a retraction movement, i.e. a lifting movement, at least a piston loa, wherein the cam surfaces 14 on the executing a lifting movement Pistons address loa and cooperate with them to cause a rotation of the shaft 2. When the gas lamellas 54a and 52a move away from each other and that by the combustion of fuel in the annular space 50, oil from the cylinder 22a can be in the hydraulic space 25 flow, and thereby the piston loa can retract into the cylinder 22a. if conversely, the gas lamellae 52a and 54a are made to move towards each other to move, by burning fuel in the annular space 50, oil from the hydraulic chamber 25 is pushed into the cylinder 22a to the piston 1oa to apply and to move it to the outside of the cylinder 22a. the Reaction between the piston 10 and the cam guide 12 leads to rotation of the shaft 2, and the shape of the cam surface 14 is provided so that the piston loa traverses a sinusoidal path around the axis of shaft 2. The gas fins 52a and 54a migrate towards and away from each other in a steady sine waveform, as a result of their hydraulic connection via the hydraulic lamellae 28a and foa with the movement of the piston loa. The acceleration forces that normally occur in rotary motors of this type, are thus due to the sinusoidal Movement of the parts greatly reduced.

The acceleration forces are further reduced as a result of the fact that the rotors are each provided with four gas blades and four hydraulic blades are what has the consequence that the rotors only have a relatively small one Swing through angles.

The rotor 4 is provided with four gas lamellae 52 which are set at 900 against each other are offset, and it also has four corresponding oil or hydraulic lamellae 28, which also extend away from the ring 24 at right angles to one another. Correspondingly, the rotor 6 has four gas lamellae 54 which extend from the ring 36 extend outside, also four hydraulic lamellae 30, which extend from the ring 36 inward extend. The gas lamellae and the hydraulic lamellae are around 900 against each other offset.

The drive means of the illustrated embodiment comprise eight drive parts lo, which are designated in the drawings as loa to loh, as well as eight drive parts 11, which are designated as parts iia to lih. These parts are in response to oscillatory rotation of the rotors 4 and 6 relative to one another in reciprocating motion. The drive parts lo and 1i are each provided in the form of spherical pistons, each of which attack curved surfaces 14 and 15 of curved guides 12 and 13, respectively.

The curved surfaces act on the spherical pistons and speak to them responds to the reciprocating motion of the spherical pistons in order to lead to a rotation of the shaft 2.

The curved guide 12 has four curls 16 distributed around the circumference which protrude radially inward towards the axis of the shaft 2 and four radially inward Curve parts 18 of the curve surface 14 form. The curve guide 13 is designed to be identical to this in terms of its shape is aligned in phase with the curve guide 12 of the shaft 2 opposite. The curve guidance 13 thus has four cams 17 distributed over the circumference, the four extending radially inwards Form extending curve parts 19 of the curve surface 15. To the radially to inwardly extending curve parts 1.8 close radially outwardly directed Curve sections 20. At the curve parts 19 directed radially inward follow curve parts 21 directed radially outward. The drive parts or pistons 11 are thus each radially extendable, while they are radially from one inwardly extending part 18 or 19 to the adjacent, radially towards outwardly extending part 20 or 21 migrate, and they are radially retractable, while they are from a radially outwardly extending portion 20 or 21 to adjacent, radially inwardly extending part 18 or 19 migrate, while the pistons travel around the axis of shaft 2.

The drive parts or ball pistons loa to loh sit in the open Ends of cylinders 22a to 22h. The spherical pistons 11a to 11h are seated accordingly in the open ends of cylinders 23a to 23h, respectively. The pistons 1o and 11 are at a standstill from the open end of the respective cylinder and are in contact with the corresponding piston areas 12 and 13. The pressure in the cylinders that control the spherical pistons 1o and 11 in the direction to on the outside away from the axis of the shaft 2 applied, leads to the creation of a reaction force between the spherical piston and the associated curve surface. This reaction force has a tangential component, which sets the shaft 2 in rotation, namely as a pole of the system of the spherical piston on the side walls of the corresponding cylinders, which are fixed opposite the shaft 2 are arranged. The cam guides 12 and 13 are profiled so that the centers the balls 1o and 11 follow a sinus wave movement, which constant a circle Superimposed on the radius while the balls are around the axis of the shaft 2 with a constant Rotate angular velocity with the shaft 2.

According to the illustration in Fig. 4, the centers of the balls follow the piston 11a to 11h of a sine wave movement superimposed on a circle Y of constant radius is, the dash-dotted line represents & estellt, while the balls 11 a lifting movement and at the same time ntieren around the axis of shaft 2.

According to the illustration in Fig. 1, the cylinder 22a is hydraulic with the cylinder 23a via the space 25 in connection.

The cylinders 22a and 23a thus form with their corresponding spherical pistons loa and 11a form a closed hydraulic circuit with space 25 via openings 42a and 43a and the associated receptacles 44a and 45a provided in the shaft 2 are.

If, consequently, hydraulic oil is pressed out of the space 25 through the channels formed by the openings 42a, 43a and the recesses 44a and 45a Sifldp are the pistons loa and 11a is applied so that it is radial the axis of the shaft 2 opposite to migrate to the outside. When a rotation of the shaft 2, cylinder 23 and piston 11 as shown in Pig. 4 to the right is believed to be when the piston lid is most radially inward Point m of the curve section 19 of the cam 17 wanders past, hydraulic oil from the room 25 pressed into the cylinder 23d, also into the associated cylinder 22d (Fig. 2), so that the reaction force between the piston lid and the flat surface of the portion 19 is left from point m in Figure 4 has a tangentially directed force component that the wave 2 set in rotation by the piston lid resting on the walls of the cylinder 23d. The situation is identical with the associated piston iodine and the cylinder 22d as shown in Fig. 2, except that the rotation in opposite Direction as shown in Pig. 2 takes place, i.e. to the left. With the other When the piston lid and iodine are raised, the piston lid moves to the right as shown in Pig. 4 in the direction of the following, radially outwardly extending part 21, until it has moved up to its end position, in which it is most radially the farthest outer point n as shown in FIG. 4 arrives.

When the piston lid has reached its upper end position, it is off the position shown in Fig. 4 to point n on the radially outwardly extending Part 21 of the Earventlä ¢ he 15 or migrated into the position of the piston lic, which in Fig. 4 is shown. With the further movement of the piston lid after to the right past point n, the cam surface pushes the piston inwards, so that the Volume of the cylinder 2Sd is reduced, which is available for the hydraulic oil stands.

Consequently, the hydraulic oil produced by the retraction of the piston lid is displaced into the cylinder 23d through the openings 43d and the recesses 45d return to room 25. The corresponding work sequence goes through the same work sequence Flask iodine.

According to the illustration in FIG. 3, the rotor 4 has four oil lamellae 28a, 28b, 28c and 28d, which are offset from one another by 90 ° and radially from Ring 34 of the rotor 4 are directed inwards. Like the one shown in Figures 1-4 Embodiment is shown, are the inner ends of the hydraulic oil lamellae 28 in sliding and sealing contact with the outer surface of the shaft 2. Correspondingly the rotor 6 is provided with four hydraulic lamellae 30a, ob, oc and od, which are extending radially inward from ring 36 and having their inner ends sliding in and sealing contact are located on the outer surface of the shaft 2. The rotors 4 and 6 are therefore rotatably mounted on the shaft 2, through the respective oil lamellae 28 and above

In the embodiment shown in Figs. 1 to 4, the end wall parts form 38 and 40 flywheels, which are arranged at an axial distance on the shaft 2 and non-rotatably with the shaft 2 are connected, i.e. with the wave 2 turn. The openings 42a to 42h and 43a to 43h are in the flywheels, respectively 38 and 40 are provided to provide a connection between the respective cylinders 22a to 22h and 23a to 23h and the hydraulic space 25. The periphery of the flywheels 38 and 40 is provided with peripheral sealing elements 38a and 40a, respectively, in order for a sliding and sealing engagement with the inner surface of the cylindrical wall 49 of the water jacket to care. The hydraulic lamellae 28 and 30 each extend over the full axial length between the inner surfaces of the flywheels 38 and 40 and act together to divide the hydraulic space 25 into eight segment chambers 32. the The hydraulic lamella 28a of the rotor 4 thus interacts with the hydraulic lamella 30 of the rotor 6 together to make the movable walls of an extendable and collapsible To form hydraulic chamber 32a. The chamber 32a is above the openings 42a and 43a and the associated recesses 44a and 45a with the cylinders 22a and 23a in communication. Accordingly, the hydraulic lamella 28a with the lamella Sob together to one To form hydraulic chamber 32b, which is with the cylinders 22b and 23 in communication. The lamellae 3ob and 28b form a hydraulic chamber 32c, which over the openings 42c, 43c and the recesses 44c, 45c in connection with the cylinders 22c and 23c, respectively stands, etc.

In the in Pig. 3 are the position of the rotors sentence Hydraulic chambers, the chambers 32a, 32c, 32e and 32g, in their closed Positions in such a way that their respective pistons loa, lla, loc, lic, ioe, ile, log and lig are in their radially raised positions and are furthest in the radial direction outer points of the curve portions extending radially outward 20 and 21 of the cam surfaces are in contact. The other set of hydraulic chambers, the chambers 32b, 32d, 32f and 32h are in their extended positions, and the corresponding Pistons 7ob, lib, iodine, imid, lof, llf, loh and ilh are consequently retracted and lie at the radially innermost points of the inwardly extending ones Curve sections 18 and 19 of the respective curve guide.

With the wandering of the hydraulic lamellae 30a and 28d in the direction of one another hydraulic oil is pushed from the chamber 32h into the cylinders 22h and 23h to to pressurize the pistons loh and lih and raise them radially. Simultaneously the adjacent chambers 32a and 32g move to both sides of the chamber 32h apart, since their respective edges 28a, Soa and 28d, 3od move away from each other, so that the respective pistons loa, ila and iod and lid in the direction of the axis of shaft 2 move back. With the closing of the respective chamber 32, what to do with it leads to the fact that the displaced oil moves up the associated pair of pistons lo and 11, drive the adjacent chambers on both sides of the converging chamber accordingly apart, so that the respective pistons lo undil drive back and the same volume of oil from the cylinders into the diverging chambers lead back.

In Fig. 2, the pistons io are shown in a dead center position.

When turning from the position shown in FIG. 2, four of the pistons move constantly up while the other four pistons retract at the same time. With the When a piston is extended, the adjacent pistons move on both sides of the extending piston so accordingly as a pole of their abutment on the radially inwardly extending part of the curved surface. On the drive shaft 2 is thus by the reaction between the pistons 10 and 11 on the respective cam surfaces 14 and 15 transmit a movement. The associated pair of cylinders 22 and 23 cooperates with the respective pistons lo and ii with one of the chambers 32, to form a closed hydraulic system, the pistons having movable walls of the closed hydraulic system, radially in response to the contraction the associated chamber 32 can be extended to the corresponding volume of the respective Cylinder to enlarge. A subsequent expansion of the associated chamber 32 allows a radial retraction of the piston in order to correspond to the volume of the associated Shrink cylinder.

As shown in Fig. 3, the outer surfaces of the rings act 34 and 36 with the inner surface of the wall 49 of the water jacket and the inner surfaces of the flywheels 58 and 40 together to form an annular gas space 50 to form the into eight segment-shaped gas chambers by sitting next to each other Pairs of gas fins 52 and 54 is divided. The gas lamellae 52a and 54a work together, to form the movable walls of an expandable gas chamber 55a. Corresponding The gas lamellae 52a and 54b act together to extend the movable walls of a and to form collapsible gas chamber 55b within annular gas space 50.

The gas chambers 55c, 55d, 55e, 55f, 55g and 55h are respectively through adjacent pairs of gas lamellae 52 and 54 are formed. According to the illustration in Fig. 3 the Galamellen each form a radial extension of a corresponding one Hydraulic lamella. For example, the gas lamella 52a forms a radial extension the hydraulic lamella 28a, and the leading and trailing surfaces of a gas lamella 52a lie in the same plane as the corresponding leading and trailing ones Areas of the associated hydraulic lamella 28a. Furthermore, the leading and trailing surfaces of the gas lamellae and the hydraulic lamellae in radial planes parallel to the axis of the shaft. They diverge from one another from the axis of the shaft towards the outer cylindrical wall of the room So that of the inner surface the wall 49 is formed.

As shown in Pig. 3 is the gas chamber 55a of the hydraulic chamber 32a assigned so that the hydraulic chamber 32a collapses when the gas chamber 55a is contracted, and that the hydraulic chamber 32a moves apart when the gas chamber 55a moves apart. The gas chambers 55b, 55d, 55e, 55f, 55g and 55h are assigned to the respective hydraulic chambers 32b to 32h. From Fig. 5 it can be seen that when the gas fins 54a and 52a by pressure in the gas chamber 55a are pushed apart so that the chamber 55a moves apart, the hydraulic chambers 32a, 32c, 32e and 32g, respectively, with the associated gas chambers 55c, 55e and 55g move apart. Conversely, the chambers 55b, 55d, 55f and 55h travel together the associated hydraulic chambers 32b, 32d, 32f and 32h together accordingly. the Expansion. of the gas chambers 55a, 55c, 55e and 55g goes hand in hand with the retraction the piston 10a, ila, loc, ilc, lote, ile, log and lig, and'that goes hand in hand corresponding, equal extension of the pistons lob, body, iodine, imid, lof, 11f, loh, lih.

Ignition devices 64a and 64b sit in the cylindrical water jacket at top and bottom dead center opposite the annular space 50. These igniters can be provided as normal spark plugs or glow plugs. Two suction openings 66a and 66b are in the standing water jacket at diametrically opposite points intended. The suction opening 66a is in the lower part of the upper right quadrant as shown in Fig. 3, while the Intake port 66b is in the upper part of the lower left quadrant as shown in FIG. There are two outlet openings accordingly 68a and 68b in the outer wall of the motor housing at diametrically opposite one another Molded in places. The outlet opening 68a is in the upper part of the lower right-hand quadrant as shown in Fig. 3 and is through a partition 65 separated from the suction port 66a. The outlet opening 68b is in the lower part of the upper left quadrant and is from the intake port 66b separated by a partition 67. If the slats are as shown in Fig. 3 rotate to the left, the respective lamella first migrates at the ends of the outlet openings 68a and 68b, which are farthest from the respective partition wall 65 and 67 are away, and then the lamellae migrate on the suction openings 66a and 66b over, from the ends of the suction openings that are attached to the respective partitions 65 and 67 lie, in the direction of the ends of the suction openings, which are closest to the respective igniters 64a and 64b. The front one The end of the respective suction opening is therefore approximately 900 in relation to one of the ignition devices offset, and the rear end of the respective outlet opening is about 900 open the opposite side of the respective ignition device of this opposite to offset. When both rotors to the left opposite shaft 2 and the stator part Rotate the motor as shown in Fig. 3, the chamber is from the is formed on wings 52 and 54 to be migrated to one another, with the outlet opening 68b in connection when a gas lamella 54 on a gas lamella 52 in the upper left Quadrant migrates to, and gases within chamber 55 in the upper left quadrant are pushed out through the outlet opening 68b after the leading lamella the chamber has migrated past the forward end of the outlet port 68b. A corresponding Situation occurs in the lower right quadrant as shown in Fig.), where the chamber 55, which is formed by the gas lamellae 52 and 54 which move towards one another is, releases its contents through the outlet opening 68a after the leading lamella of the chamber has migrated past the forward end of the outlet port 68, i.e., the The end of the outlet opening 68a which is furthest away from the partition wall 65.

Starting with the dead center position shown in FIGS. 2, 3 and 4 the gas chambers 55a and 55e both in the closed state and stand with the spark plugs 64a and 64b in connection. The gas chambers 55d and 55h have moved apart and communicate with outlet ports 68a and 68b, respectively. The gas chambers 55c and 55g are located immediately in front of the front ends of the suction ports 66a or 66b and immediately behind the rear ends of the outlet openings 68a and 68b, respectively. The gas chambers 55b and 55f are provided with the suction ports 56a, respectively and 56b in connection, wherein the trailing lamellae 54b and 54c are the rear Approach ends of the respective suction ports 66a and 66b. When the chambers 55a and 55e each contain a compressed charge of fuel, ignition takes place of the compressed fuel charges in the chambers 55a and SSe when a connection with the spark plugs 64a and 64b occurs, and the resulting increase in pressure as a result the combustion of the fuel pushes the adjacent wings 52a, 54a and 52c, 54c apart, with the result that chambers 55a and SSe are in one working stroke.

With the further turning of the rotors in the direction to the left opposite the stator and opposite the rotating shaft 2, the gas lamellae 54a begin, 54b, 54c and 54d to move the gas lamellae 52d, 52a, 52b and 52c to a Beginning of the closing of chambers 55a, 55f, 55d and 55b and a corresponding one To cause expansion of the chambers 55a, 55g, 55e and 55c. A load of fuel enters the chambers 55b through the suction port 66a, and with walking by the trailing gas lamella 54b of the chamber 55b at the rear end of the suction opening 66a and the approach to the leading gas lamella 52a of the chamber 55b is the Fuel charge compressed as a result of the collapse of chamber 55b.

The same state prevails in chamber 5Sf at the same time.

With the turning of the chambers as shown in Fig. 3 to the left The chambers 55b begin around the ashes of the shaft 2 from the position shown in FIG. 3 and 55f to collapse in one compression stroke.

Chambers 55c and 55g following chambers 55b and 55f begin expand as they migrate to the left from the position shown in FIG. As the leading lamellae 54b and 54d of the chambers 55c or 55g at the front ends of the respective suction port 66a and 66g for manufacture a connection between the suction ports and the chambers 55c and 55g begin the chambers with the reception of a fuel charge, so begin with an intake stroke.

As the rear surfaces of the leading gas lamellae wander past 52b and 52d of the chambers 55d and 55h, respectively, at the front ends of the respective outlet ports 68a and 68b, the chambers 55d and 55h are in communication with the outlet, and these Chambers begin a discharge stroke and displace the burnt gas that is in them is contained, through the outlet openings, while they are out of the one shown in FIG Move together.

With the ignition in the closed chambers, which are attached to the upper and lower dead center positions are, so a set of hydraulic chambers is 52 made to expand and the other set of hydraulic chambers will made to contract. In the position shown in FIG Ignition in the chambers 55a and 55e that the hydraulic chambers 32a, 32c, 32e and 52g move apart and that the hydraulic chambers 32b, 32d, 32f and 32h accordingly move together to lob and body a simultaneous radial extension of the pistons, lod, lid, lof, lif and loh and 11 and a corresponding radial retraction of the Pistons loa, iia, loc, llc, loe, ile and log, lig from their positions shown in FIG. 2 to effect. With the simultaneous explosion in the upper and lower Dead center of a collapsed chamber that is connected to the spark plugs, oil is pressed out of a set of hydraulic chambers, namely the hydraulic chambers, which are at 45 degrees on either side of the ignition devices. This oil can nowhere else to go except that the two associated spherical pistons lo and ii be pressed radially outwards against the cam guides. The hydraulic chamber begins to contract while the associated spherical piston is at the point walk past the curve guide where the ball pistons have the smallest distance from the axis, i.e. the positions that the spherical pistons lob, leib, led, imid, lof, ran, loh and lih in Fig. 2 and 4 take. The inclination of the curved surfaces in the reference on the Radius vectors of the spherical piston ensures a tangential directional component of force which the balls against the sides of the associated cylinder pushes to apply torque to the flywheels at eight points. Except for these effective working torques all other forces are radial and tangential balanced so that there is no vibration or undue stress on the main bearings of shaft 2.

In the illustrated embodiment, the flywheels are each provided with eight bolts 70a, 70b, 70c, 7od, 7oe, 70f, 70g and 70h, respectively protrude into the gas chambers 55a to 55h. The bolts 70 are from the flywheels before, and their job is to synchronize the rotors and the two each adjacent hydraulic lamellae 28 and 30 on the respective oil openings 42 and 44 and the recesses 43 and 45 in the closest approach of the slats keep centered. For example, the bolt 70a holds as shown in FIG Fig. 3 the lamellae 28a and 3oa opposite the openings 42 and 44a in the next Approach of the gas lamellae 52a and 54a centered. Practice after starting the engine the lamellas do not exert any net force on the bolts 70 to rotate the flywheels, and the two adjacent lamellae approach the bolt 70 and wander away from them, in a symmetrical sine waveform that excepted around 1800 Phase so that there is no net torsional vibration affecting the flywheels 38 and 40 is awarded while the flywheels with a constant Rotate angular velocity.

According to the illustration in Fig. 1, the shaft 2 has stepped end portions 86 and 88 which are rotatably seated in bearings 9o and 92, respectively. The warehouse 9o sits in the outer end wall 94 of the motor housing and the bearing 92 sits in the outer end wall 96 of the motor housing. The end walls 94 and 96 are hollow to give space 98 or 100 for water or another coolant. Accordingly has the cylindrical water jacket has a space 102 between walls 48 and 49 for receiving of water.

Annular grooves 104 and 1o6 are each molded into the end walls 94 and 96, which are connected to oil inlet channels 108 and 11o, respectively. The respective cylinder 22 and 23 are provided with inlet ports 112 and 113, respectively, which correspond to the respective Grooves 104 and 106 is in communication. Check valves 114 and 115 regulate the Openings 112 and 113. Hydraulic oil can therefore constantly through the channels 1o8 and 11o are fed to the hydraulic circuit to compensate for leakage to the Creating ball butt over. The respective cylinder is then added to each other Oil fed when the pressure in it is below the pressure in the respective grooves 104,106 falls off.

In Pig. 5a to 5i are schematic of the positions of the gas lamellae during one 400 rotation of the shaft and flywheels. In the illustrated embodiment the slats have a norminal width of 200, i.e. the front and rear Plates of the lamellae as shown in FIG. 5 and as shown in FIG FIGS. 5a to 5i diverge at an angle of approximately 200 to one another. In reality the slats have a width slightly less than 200 to provide space for compacted food To create gas between two consecutive lamellas. Hence take two lamellas about 400 of the annular gas space 50, so that 500 for a working displacement remain. An index radius for shaft 2 and flywheels 58 and 40 goes through the bolt 70a.

In Fig. 5a, the lamellas lying in the top dead center are shown, with the shaft and flywheel index radius going through top dead center. the Chambers 55a, 55c, 55e and 55g are fully closed and chambers 55b, 55d, 55f and 55g have moved completely apart. The chambers 55b and 55f are with the Suction ports communicate, and the chambers 55d and 55b communicate with the discharge ports in connection. The chambers 55a and 55e each contain a compressed fuel charge, while chambers 55c and 55g have just completed a displacement stroke With simultaneous ignition in chambers 55a and 55e to expand those therein For fuel loads, the lamella 54a begins before the index radius through the bolt 70a to advance and the sipe 52a begins to recede from the index radius. In Figure 5b the index radius has moved 50, and so have the front surfaces of the lamellas 54b and 54d have passed the rear ends of the respective suction ports, and the fuel begins to compress in chambers 55b and 55f. The chambers 55a and 55e still run in Pig.

5b illustration shows a working stroke.

In FIG. 5c, the lamella 54a is 2.9 ° opposite the index radius moved forward, and the lamella 52a has accordingly moved back by 2.90 from the index radius, where the index radius has moved forward by 100 from top dead center.

The chambers 55a and 55e are still in the state of the working stroke, and the chambers 55b and 55f are still in the state of a compression stroke. The chambers 55c and 55g communicate with the suction ports, and the chambers 55d and 55h communicate with the outlet ports.

The chambers 55a and 55e remain in their state of a working stroke during a rotation of the shaft and the flywheel by slightly more than S according to FIG Representation in Fig. Sa. With the rear surface of the lamella 54a moving past The working stroke and the chambers end at the front wound of the outlet opening 55a and 55e begin their displacement stroke. In Fig. 5i, the chambers 55b and 55f is substantially full of a new charge of fuel, and they arrive with the appropriate ignition devices with a further turn the shaft by 5 °. An explosion occurs in each of the eight chambers with the passing of the same on the respective ignition device. Consequently there there are sixteen working strokes per revolution of the shaft. The lamellae of the respective rotors vibrate in a symmetrical sine waveform with respect to the wave, like that through the symmetrical arrangement of the lamellae in relation to the index radius in Fig. 5a to 5i is displayed.

In Fig. 6 * graphically the sinusoidal movement of the slats opposite the flywheels and the shaft 2 shown. In Fig. 6 is the rotation of the shaft or the flywheel on the horizontal axis, while the positions of the Center lines of the slats are plotted on the vertical axis. Figure 5a, for example shows the center line of the lamella 54a at a position of 100 beyond the upper one Dead center with a rotation of the index radius of 00. The curve A in Fig. 6 shows the center line position of the lamella 4a with respect to the flywheel index radius during the rotation of the flywheel and the shaft. After a rotation of the flywheel index radius the lamella 54a has moved forward by 10 ° to a position that is 12 aO before the Flywheel index radius is, and the fin 52a is in a position back- * is gave way, which is 12.90 behind the flywheel index radius.

The middle position of the lamella 54a is 22.5 ° in front of the flywheel index radius, and the middle position of the lamella 52a is 22.50 behind the flywheel index. The lamella 52a and 54a are 45 ° with a 22.50 and 67.5 ° rotation of the shaft and - rotation of the flywheel index radius, also at every successive 45O in the diagram. The respective lamella thus swivels by plus minus 12.50 around the middle layer around. When the shaft is rotated by 0 °, the lamella 54a therefore lies by 12.50 behind its middle position, and the lamella 52a is about 50 in front their middle position. If the shaft rotates 450, the distance is between the lamella center lines 700. The deviation of the respective lamella from its mean Location is only about a quarter of 500, which is a significant reduction the acceleration forces that normally occur in a motor of this type.

The trigonometric equation for curve B in Fig. 6 is: Y ° = 22.5 ° + X ° + cos 4 x °. The general form of this equation is, expressed in Arc units: Y = 11 + e + D cos 46 2N where e is the angle X divided by 57, j is, N is the total number of blades of both rotors and D is the displacement angle is. By differentiating in order to establish the speed: dy = 1 - 4D sin 48. Since Sin 4 # IitmalN exceeds one, the speed is always uj @ i @@, w @ nn D is less than 1/4 arc unit or 57.5 = 14.30. In Fig. 6, D is 12.50, and consequently the rotors always have a positive speed, which means that they are never stopped in their forward movement.

In the schematic representations shown in FIGS. 5a to 5i the slats each 200 thick. Two such lamellas take up 400 of the combustion chamber so that 500 remains for a displacement in the respective quadrant. Of the The respective set of slats swings by plus minus 12.50 compared to the middle one Position per 450 shaft rotation.

A four-stroke combustion cycle goes between two lamellas take place per 1800 shaft rotation. There are two working strokes per chamber and rotation, which gives a total of 16 working strokes per revolution of the while.

With the movement of the index radius of the shaft by 450 from the range shown in Fig. 5a, i.e. with the twisting of the shaft by 450, the lamella 54a moves forward by 700, while the lamella 52a only moves forward by 200. In the next 450 rotation of the shaft, the lamellae 52a, b, c and d rotate by 700 while the lamellae 54a, b, c and d only extend by 200. Rotate both sets of lamellas but constantly move on in the same direction. None of the lamella sets interrupted its rotation after on the left opposite the motor housing according to the illustration in Fig.

5a to 5i, rather the individual slats vibrate in a steady manner Sine wave movement relative to each other.

In the embodiment of the invention shown in Figs are parts similar to the parts in the embodiment shown in Figs are identified by the same reference numbers increased by 100. The rotors 104 and 1o6 in Fig. 7 thus correspond to the rotors 4 and 6 in Fig. 1, rings 134 and 136 in FIG. 7 correspond to rings 34 and 56 in FIG. 1, the annular gas space 15o in FIG. 7 corresponds to the annular gas space 50 in Fig. 1 to 4 etc.

In the embodiment shown in Fig. 1, the end walls of the annular gas space 50 formed by the flywheels 38 and 40. In the one shown in Fig. 7 on the other hand, the end walls of the annular Gas space 150 formed by fixed annular end wall parts 302 and 5o4, the extending radially inward from the inner surface 149 of the outer cylindrical wall 148 extend. The annular end wall portions 302 and Do4 are cylindrical with the outer one Wall connected, and they are hollow to form spaces 306 and 308 for a coolant, respectively. The outer cylindrical end surfaces of the rings 134 and 136 are in sliding and sealingly abut the inner surfaces of the annular end wall portions 302 and 5o4 likewise on the respective flywheel parts 140 and 138. Ring seals 31o tid j12 are provided on the end wall parts 5o6 and 5o8, respectively, in order to connect to the to attack adjacent end walls of the rings 134 and 136, respectively. As in the first exemplary embodiment parts 138 and 140 form the end walls of the annular hydraulic space 125 in FIG Fig. 7. Part 138 is provided with openings 142a-h and 145a-h, respectively the openings 42a to h and 43a to h in the embodiment shown in FIGS. 1 to 4 correspond.

The rotor 104 has an inner bearing bush 714 which is concentric to the Bearing ring 134 arranged and with the inner ends of the hydraulic lamellae 128a b, c and d of the rotor 104 is connected, which the hydraulic blades 28a, b, c and d in the one shown in Fig.

1 to 4 correspond to the embodiment shown. Is accordingly the rotor 1o6 is provided with a bearing bushing 316, which is attached to the inner ends of the hydraulic lamellae 130ast, c and d is attached, each of which is attached to the slats oa, b, c, d in the in FIGS. 1 to 4 correspond to the embodiment shown.

Sockets 314 and S16 are in an end-to-end position, and they are rotatably mounted on the shaft 1o2. The inner, adjoining cylindrical ends of the bushings 514 and 516 are thus in sliding and sealing abutment against one another, and the outer surfaces of the bushings 514 and) 16 act together to form the inner cylindrical surface of the annular hydraulic space 125 to build.

Cylindrical bearings 318 and 320 correspond to bushings 514 and 516, respectively fixed opposite, and they can be made of bronze or a similar material exist. Inner annular grooves 322 and 324 are respectively in the adjacent or opposite ends of the bushings 314 and 316 are provided and cooperate around an annular recess 326 between sockets 314 and 316 and the outer surface to form the wave 1o2. On the socket 514 there is a bevel gear ring 328, which is in the recess 326 protrudes. A corresponding ring gear 53o sits on the socket 516. The ring gears 328 and 330 mesh with pinions 332 which are rotatable on peg wire 3) 74 are mounted, which are connected to the shaft 1o2 and protrude radially from it. The ring gears 328 and 3so connect the rotors together with the pinions 332 104 and 1o6 with the shaft 102 to keep the rotors and the shaft in sync with each other to hold while the rotors oscillate against each other and rotate around the axis of the shaft 1o2 in the way that the rotors 4 and 6 do in the embodiment shown in Figs. ulenn one such Gears 328, 53o and 334 are provided, no pins 70 need to be provided be, as is the case in the embodiment shown in Figs. In the embodiment shown in FIG. 7, the transmission 328, 530 and 334 provides for a positive synchronization between the rotors 104, 1o6, the shaft 1o2 and the spherical piston 11o and 111. The gas lamellae 152 and 154 and the hydraulic lamella 12 .. and 131 in uem v Fig. 7 are shown in the embodiment forced by the gearbox B28, 330, 332 to be symmetrical of the shaft to swing opposite, and they are thereby positively locked in on all sides Kept in phase with the wave.

In the one in Pig. 7 is an outer combustion chamber 340 is provided in a combustion case 358a, which is located at the top dead center. A corresponding combustion housing 938b is located at bottom dead center or at the diametrically opposite point compared to the combustion case 538a. The combustion chamber 340 can be refractory lined and therefore under white-hot temperatures remain while the engine is running. The combustion chamber 340 stands with the annular Gas space 150 via an inlet opening 342 and an outlet opening 344 in connection. The inlet opening v42 and the outlet opening 344 stenen with the annular gas space 150 at peripherally spaced locations as shown in FIG is. The inlet port 342 is located immediately before top dead center according to FIG the representation in Pig. 8, and the outlet port 344 is immediately in FIG Connection to the top dead center.

With the rotation of the chamber 155a about the axis of the shaft 1o2 in the direction of to the right as shown in Fig. 8 so it comes in connection with the outer brelm chamber 40 via inlet port 342 as soon as the trailing End of the front gas lamella 152a, the rear end opening 542 passed so that the air in the chamber 155a is compressed into the combustion chamber 540 through the opening 342 is depressed. When the chamber 155a is the top dead center position as shown Reached in Fig. 8, the front end of the rear gas blade 154a has the front or the right-hand end of opening 542 to close opening 342, and the chamber 155a is brought out of communication with the two ports 42 and 544. When the gas chamber 155a is in the top dead center position, it is at a standstill no longer in connection with the combustion chamber 340. At this point, a Combustion take place in the combustion chamber, with fuel from outside entering the white hot chamber is injected.

As soon as the gas chamber 155a is somewhat above the top dead center position according to 8, the chamber 155a comes into communication with the combustion chamber 340 via the outlet opening 544. The white pressurized gases can then return to chamber 155a through outlet port 544. At from the combustion chamber 340 in the top dead center position is separated gas chamber 155a the severity of the explosion on the outer chamber) 40 is limited to a noise level and to reduce stress on the engine parts. Furthermore, the gases can with the Fuel that is injected into the combustion chamber 54o from the outside swirls and be mixed, and no Fuel can be in any of the Combustion chambers 155 between the respective gas lamellas 152 and 154. The fireproof lined chamber can remain in the white hot state to ensure continuous Ensure ignition, since the chamber 340 the cooling effects of the displacement, Intake and compression strokes suspended.

In Fig. 7, a rotary motor is shown, consisting of means, which form an annular gas space 150 which has an outer cylindrical wall 149 has a shaft 1o2 and two rotors 104 and 1o6, each for rotating the shaft 1o2 opposite and supported against each other to perform an oscillating rotation are. Gas lamellae 152 and 154 are provided on rotors 104 and io6, which protrude into the annular gas space 150 in such a way that two side by side Gas blades 152 and 154 cooperate to form the movable walls of a collapsible Gas chamber 155 to form. The two adjacent slats 152 and 154 migrate toward and away from each other to toward the gas chamber 155, respectively enlarge and reduce that is formed between the slats in Response to the oscillatory movement of the rotors 104 and 1o6 against each other with the Rotate the rotors around the axis of the shaft 1o2, thereby opening the gas chamber 155 that is in between is formed to reduce and enlarge, respectively. An outer combustion chamber 340 is arranged on the engine and has an inlet port -542 and Outlet opening 344, which are arranged with the annular gas space 150 at the peripheral distance Bodies are connected.

The respective gas chamber 155 is thus one after the other with the Combustion chamber 340 in communication if the space between the forward and the rear Lamella 152 and 154 is only in communication with inlet port 342 while the gas chamber 155 approaches its fully compressed state, then is separated from the combustion chamber 340 when the trailing end of the front fin 152 and the leading end of the trailing fin 154 between the inlet and the outlet opening, while the gas chamber is fully closed in its position as shown in FIG State reached, and finally with the combustion chamber 740 is in communication when the space 155 between the leading and trailing lamellae 152 and 154, respectively is only in communication with the outlet opening 544, while the gas chamber 155 is seen begins to expand from its fully contracted position.

Claims (19)

Pat ent ans p rüch e 1.Rotary machine, g e k e n n n z e i c h n e t d u r c h means, which form a hydraulic circuit and which include a space for hydraulic fluid, who is turned on in the circle, one in response to the flow of fluid in the room and out of the room in the circle rotatable cell, two rotors, each to rotate the shaft opposite and to perform an oscillating rotation relative are mounted to each other, and on the oscillatory rotation of the rotors relative to each other responsive means for causing hydraulic fluid to flow into the Space and out of space. 2. Rotary machine according to claim 1, g e k e n nz e i c h n e t d u r c h an inlet port for connecting the hydraulic circuit to a source of pressurized hydraulic fluid and a valve to prevent a flow of hydraulic fluid from the hydraulic circuit through the inlet channel, however, to allow hydraulic fluid to flow into the circuit the inlet channel is established when the pressure from the source is higher than the pressure is in the circle. 3. Rotary machine according to claim 1, d a d u r c h g e k e n n z e i c h n e t that the responsive to the oscillatory rotation of the rotors means a Number of Ilydrauliklamellen in the room, which when the rotors vibrate are movable relative to each other, such that a flow of hydraulic fluid is effected in and out of space. 4. Rotary machine according to claim S, d a d u r c h g e k e n n z e i c h n e t that the hydraulic lamellae are each replaced by two sets of hydraulic lamellae are formed, one of which is set by one of the rotors and the other of the other of the rotors is carried. 5. Rotary machine according to claim 4, d a d u r c h g e k e n n z e i c h n e t that the hydraulic slats to form a number of expandable and Collapsible chambers cooperate in the room, with two adjacent Hydraulic lamellae form the movable walls of one of the chambers and create a vibration of the rotors causes one set of the chambers to diverge while the other Set of chambers closes accordingly. 6. Rotary machine according to claim 5, g e k e n nz e i G h n e t d u r c h means which form a channel for the respective chamber, such that a Medium in the chambers and out of the chambers when moving apart or moving together of the chambers. 7. Rotary machine according to claim 6, g e k e n nz e i c h n e t d u r c h Drive means that act on a flow of medium in and out of the room respond to cause rotation of the shaft. 8. Rotary machine according to claim 7, d a d u r c h g e k e n n z E i c h n e t that the drive means comprise at least one drive part, the liftable in response to the flow of medium into and out of space is, wherein means are provided which respond to the lifting movement of the drive part, such that rotation of the shaft is caused. 9. Rotary machine according to claim 7, d a d u r c h g e k e n n z e i c h n e t that the drive means have at least one drive part for the respective Include chamber that in response to the flow of medium into the associated Chamber and is stroke movable from the associated chamber, such that a rotation of the Wave evoked will. 1o. Rotary machine according to claim 9, d u r c h g e k e n n z It is noted that the drive means further comprise means which act on the lifting movement the drive parts respond in such a way that the shaft is set in rotation. 11. Rotary machine according to claim 1o, d a d u r c h g e k e n n indicates that the means that respond to the lifting movement of the drive parts, are formed by a curve guide with an endless curved surface, which a Forms counterpart to the drive parts in such a way that during a lifting movement of the drive parts the shaft is set in rotation. 12. Rotary machine according to claim 11, d a d u r c h g e k e n n z e i c h n e t that the point opposite to the drive parts is non-rotatably arranged is such that the drive parts rotate with the shaft. 1 rotary machine according to claim 12, d u r c h e k e n n z e i c h n e t that the shape of the cam surface is provided so that the drive parts traverse a sinusoidal path, the drive parts with the shaft around the Axis of the cell Jlerulfi rotienl. 14. Rotary machine according to claim 1D, d a d u r c rl g e k e n n z e i c h n e t that the drive parts have a relative stroke movement in the radial direction run to the axis of the shaft with a vibratory rotation of the rotors relative to each other. 15. Rotary machine according to claim 14, d a d u r c h g e k e n n z e i c h n e t that the cam guide with cams arranged at a peripheral distance which extend in the direction of the axis of the shaft and radially inwardly extending curved parts of the curved surface form, the curved surface is provided with radially outwardly extending curve portions that are attached to connect the radially inwardly extending portions of the ticks in such a way that the respective drive part can be radially extended, while it extends radially from one inwardly extending part to the adjacent, radially outwardly extending part Part migrates, and is radially retractable, while it moves radially from a outwardly extending part to the adjacent, radially inwardly extending part Part moves while the drive part rotates around the axis of the shaft. 16. Rotary machine according to claim 15, d a d u r c h g e k e n n z e i c h n e t that the drive parts are each formed by a piston and for this purpose a number of open-ended cylinders provided in a flywheel are, the respective pistons sitting in the open end of each cylinder and protrude from the respective cylinder in contact with the same cam surface. 17. Rotary machine according to claim 16, d a d u r c h g e k e n n z e i c h n e t that the respective cylinder with the respective chamber via the openings is in communication such that the respective piston in response to merging the associated chamber is radially expandable and thereby the volume of the associated Cylinder is enlarged accordingly, with a subsequent expansion of the associated chamber a radial retraction of the piston and a corresponding reduction the volume of its cylinder. 18. 1? Otation machine according to claim 1, d a d u r c h g e k e n n show that the shaft extends through space and the inner one Wall of the room is formed by a surface which is concentric to the shaft. 19. Rotary machine according to claim 18, d a d u r c h g e k e n n z e i c h n e t that the respective rotor comprises a bearing ring and that the hydraulic lamellae of the respective rotor protrude inwards from the respective bearing ring, in such a way that that the rotors are rotatably mounted on the shaft.