ENGINE WITH ROTATING CYLINDER WALL

Abstract: A piston machine, most particularly an internal-combustion machine, in which the cylinder wall performs a rotating motion round its own axis. Apertures on the cylinder wall allow it to act as a rotating slide valve, so that no valve system is needed. In the first example, the stroke movement of the piston is converted to the rotating motion of the cylinder wall (which on the same time serves as the axle of the machine) through bolts which slide or roll in linear guide-slits in the cylinder wall and curved guide-tracks on the stationary outer part of the machine. The use of the curved guide-tracks allows the adaptation of the time-law for the volume change in the working chamber, to the needs of the mechanics, thermodynamics and reaction kinetics. In the same rotating cylinder are installed two pistons of equal mass which fulfil an exactly symmetrical opposite motion, so that no free accelerating forces exist and therefore no vibrations appear on the machine. In the second example the stroke movement of the piston is converted to the rotating motion of the axle through a crank and two universal joints. The relative position of the axis of the crank and the axis of the cylinder determine the length of the stroke and in consequence its power. The crank's bearing position can vary correspondingly to the cylinder during the function of the machine, so that its power is continuously variable and even its working direction can be reversed without stopping and by constant rotating speed.

Description: Engine with rotating cylinder wall This invention relates to a machine with an inside space (working chamb which periodically changes its volume and more particularly refers to machine that is mainly used as a power engine, as pump for liquids and gases or as a compressor for gases. Such machines commonly use for their operation the stroke movement of a cylindrical piston in a cylindrical ' ole. The linear motion of the piston is converted to the rotating motion needed for most purpose with a mechanism consisting of a connecting rod and crankshaft. The motion of additional parts (valves) is needed to open and close the working chamber for the inlet and outlet of the operating fluid. A separate mechanism is required for this purpose- The advantage of such constructions is mainly t it the cylindrical working chamber can be sealed easily and efficiently. Furthermore these machines have been built for decades and reached a high degree of sophistication through a process of continual improvement. Their most notable disadvantages are: 15 The mechanism for the motion of the valves impedes (on account of its inertia) the quick inlet and outlet of the working medium and moreover is complicated, expensive and delicate. 2. The time-law for the change of the volume in the working chamber is not the best one either for diminishing the accelerating forces, nor for increasing the efficiency of the machine, but it cannot be changed since it is imposed on account of the --kinetic principle of the crankshaft.' 3« During the conversion of the linear movement to the rotational movement strong oblique forces appear on the piston that cause . great friction losses and wear. . The length of the stroke of the piston remains constant and sub¬ sequently the power of the engine, at constant rotational speed. Therefore a supplementary gesr box is needed for most applications. Numerous attempts to excape from these disadvantages have been under¬ taken and are being continuously carried out, but they are confronted with other difficulties like problems of construction, sealing and wear; or they cause reduction of efficiency. The aim of this invention is the construction of a machine which with the greatest possible simplicity fulfils the function of a piston engine without the disadvantages of the known types. I have found that the above object may be accomplished by giving to the cylinder wall and/or cylinder top a rotating motion around its own axis. This motion is used, to regulate the inlet and outlet to the chamber. Connecting opening or openings (muzzles) on the cylinder wall and/or cylinder top meet (during the rotation) on the facing stationary part of the engine: a) Channels for the inlet or outlet of the working fluid (the chamber is open, depending on the direction of the piston's movement ., ' /souuctceleeαts i-nt.ak,e.) or b) the closed wall (the chamber is closed, <3spenc3_Lngτ_si the piston's movement/ hsre /iscompression or expansion) or c) devices for an additional inlet of a fluid (e.g. injection jet) or ignition (e.g. spar lug). Fig. 1 shows these possibilities on the principle of a four stroke engine. The upper row indicates the different positions of the connecti opening, the lower row . the corresponding positions of the piston. In position" (a-) the muzzle is lined up with the inlet channel, the piston's movement causes the increase of the chamber's volume, gas streams in. In position (b) the closed wall of the immobileouter part of the engine stands in front of the connecting opening, the chamber is shut up, the piston's movement causes compression. In position (c) the piston has reached its highest point, the muzzle is in front of the spark plug, ignition takes place. In position (d) the chamber is closed, expansion occurs. In position (e) the gas flows out. The piston maintains its cylindrical form so that it can be easily seale with piston rings and can fulfil a pure stroke movement or have an ad- __OMFI : - " ' " - * - * ~- ~ ~ ~ ditional rotating motion around his own axis with the same or another angular velocity as the cylinder wall. The sealing of the connecting openings against the immobile outer part of the engine is achieved through one or more concentric sealing rings put around the muzzles of the cylinder wall and/or cylinder top. Thes rings have a round, oval or polygon shape accordingly to the form of the muzzle. The rings are pressed against the stationary part of the engine through self elasticity or by springs installed underneath. Another possibility to seal the connecting opening against the station part is to put the sealing rings (like the piston rings) over the whol periphery of the rotating cylinder wall in both sides of the connectin opening, while the space between them is tightened with sealing sticks or rolls parallel to the cylinder axis. The sealing elements can also be installed, instead of the outer side o the .rotating cylinder wall, in the inside of the stationary part of th machine. In that case they must surround all the openings of this part (inlet channel, outlet channel, devices for additional inlet and igniti or they must lie over the whole periphery in both sides of these openin The main, advantage of this invention lies in the fact that: Although the cylindrical form of the piston and the four-stroke princip have been maintained, the .engine is relieved from the valve mechanism. Consequently the invention reduces the construction and repair cost as .well as the engine's volume and weight. Furthermore the flow. condition are improved, because the opening and closing of the chamber proceeds faster since there is no need to accelerate any additional masses and the whole cross section of the connecting opening is available to the flow of the working βedium. Additional advantages depend on the. use of the engine, the engine specifications, and foremost on the manner in which the stroke of the piston is realized. If the conventional mechan of the crankshaft- is. used, this case dispenses with detailed descripti But if one desires to be relieved from the disadvantages (page 1 point ' s and 3) which the crart εhaft mechanism has in addition to its large wei and volume; or if a variable power option is pursued, I have invented constructions which bring the advantages of this invention to its full O PI - h - ' validity. In two examples herebelow such constructions are described in detail. Example 1 Fig. 2 (a and b) show an internal-combustion engine with four chambers i common cylinder 1 which at the same time is the axle of the machine. The double pistons 2 and 3 form the four chambers 4, 5, 6 and ?. The curved guides 8 and 9 are built like grooves in the stationary outer part. In these grooves slide the ends of the bolts 10 and 11 which are fixed on to the " pistons. The bolts penetrate the cylinder wal through the slits 12 and 13- When the cylinder rotates, the slits force the bolts 10 and 11 (and consequently the pistons) to rotate too. Durin this motion however, the bolts must follow the guidance of the grooves 8 and and there ore they result in a linear axial movement, which is furthered on the pistons. Axial (or combined axial-radial) bearings in both ends of the rotor carr the strong axial forces caused by the pressure in the working chamber. The mino -radial forces resulting from the weight of" the rotor are mainl distributed to the four gliding surfaces on which slide the cylinder muzzles. Therefore at these locations one must have sliding bearings or needle bearings. Lubricant is put in the space where the bolts 10 and 11 are moving. Cooling medium (water, air or oil) circulates round the rotor. Sealing rings on the proper positions separate the lubricant from the cooling medium. The mentioned bearings and tighting elements are not shown in Fig. 2. . . The fact, that the cylinder rotates immersed in the surrounding medium, permits,with appropriate form of its surface,the circulation of this medium without additional pumps or blowers. One part of the rotor works like the oil pump, another as the water pump or the blower. The bolts 10 and 11, the slits 12 and 13 and the grooves 8 and 9 compose the whole mechanism for the conversion of the linear motion of the pisto to the rotating motion of the shaft. During this conversion strong forc appear on the inside surfaces of the slits and the grooves. For this reason at these locations I have slide-bearings (as shown in Fig. 2) or roller bearings in order to diminish the friction losses. At each position, I have put two rollers, each in contact with the guide surfac The linear "guide (slits 12 and 13 on Fig. 2) and the curved guide (grooves 8 and 9 c Eig. 2) can also be constructed as guide-tracks. In this case the bearings move on the outer side of the part, and these surfaces can easily be made, hardened and polished. The mechanism "bolt, linear guide, curved guide" can also Le realized with the linear guide on the outer stationary part and the curved guide grooved on to the cylinder which is divided into two independent parts. In that case the piston has no rotating motion and the different parts of the cylinder are held in place by the axial bearings. The two parts of the Fig. 2 show the machine at two different phases during its operation. In Fig. 2b the cylinder is rotated 90° with rega to Fig. 2a. The pistons which in Fig. 2a are .in the one end of their course, have now reached the other one. The motion of the pistons is absolutely symmetrical so that no vibrations are caused from the periodi acceleration of masses. During one rotation of the cylinder wall the pistons run four times over their course, so that this machine is a " ■ four cylinder" four-stroke engine. Correspondingly four muzzles (14, 16, 20, 22) are provided in such positions so that each chamber is ir- another phase of the four-stroke cycle. The openings (muzzles) of the chamber can be round (as shown in Fig. 2) or elongated- ith their smaller dimension parallel to the rotor axis. That gives the advantage to shorten the whole length of the machine. In Fig. 2a in chamber -k the opening 1 - leaves the inlet channel 13; the compression begins. In chamber 3 the opening is in front of the spark plug; expansion begins. In chamber 6 begins the intake. In chamber 7 begins the exhaust, the opening 20 faces the outlet channel 21. In Fig. 2b the muzzle of the chamber h faces the spark plug. In chamber begins the exhaust, in chamber 6 the compression, in chamber 7 the intak A combustion engine is in reality a chemical reactor with variable volum - 6 - The change of its volume is used to produce mechanical work. Therefore the optimization of its function (complete combustion, minimization of harmfu3 exhaust gases, and higher efficiency) can only be obtained if the time-law of this volume change is adapted to the needs of the thermodyna and the reaction kinetics. In the common piston motor however, this tim law is imposed from the ' crankshaft mechanism as a sine motion. It is ea to show that this time-law is not suitable even for the acceleration of the masses. A motion in accordance with the square of the time gives the saiπe piston velocities with much smaller forces. The -use.of the curved guide in this example allows the application of th appropriate time-law, which in addition offers a higher efficiency than the sine-law. If otherwise 'the maximum efficiency is pursued, the curve guide ca produce motions with time dependency of higher order or ex¬ ponential, which are better adapted to the needs of thermodynamics and chemical kinetics. The use of the curved guide must not necessarily be limited to a four-ct engine. The machine can have, two or six or generally anydesired number o strokes. Furthermore through the use of the curved guide it is possible, that each stroke has another duration or another- length than the other.. The .machine shown in Fig. 2 has a lot of advantages. The most important 1. Unusual economy of total volume and material. As shown in Fig. 2 the total volume of the machine is only about eight tines larger than the useful working space of the chambers. 2 . . Unusual simplicity of the construction and therefore reduction of the production- cost and repair cost. The whole "four cylinder" ' engine consists of four -pieces easy to construct, namely the stationary part, the rotor and the two double pistons with their bolt 3. Unusual diminution of the friction losses- On the pistons appear only axial forces. In the places where friction occurs (linear guides, curved guides), it can be reduced through the use of ball bearings. h. Unusual possibility * to fit the time-law of the volume change in the chambers acccrdinr to the needs of thermodv__a_=ics and chemical kinetics. Therefore better efficiency, fuel economy and less harmful exhaust gasεes. The machine in Fig. 2 shows a high relation of its length to its diame because four chambers are placed one behind another. If it is desired to reduce the length of the machine, or to have only two chambers, it i not appropriate to "cut" * simply the machine in the middle and to use o one double piston, because the accelerating forces are no longer compe sated. Care must be taken that always two equal masses have an opposi motion. Fig. 3 shows such a "two cylinder" engine. The pistons 1 and 2 have a opposite motion because their bolts 3 and 4 have' an angle of 90°. Both bolts are divided in two parts and the cylinder wall has four slits 5, 7, 8 as linear guides for the bolts. The machine has only one curved guide and possesses the advantage to offer between the pistons an addit al working space 9- This space is unsuitable as a combustion chamber, but can be used for other purposes (e.g. as compressor). Fig- shows a machine in which theheight of the piston is reduced to a plate 1 connected with the bolt 2 through the spindle 3- O 11 the cylind wall is fixed the separating wall 4. The spindle penetrates the wall through a hole. ' Sealing rings in the inside of this hole seal the spi during its stroke movement through the wall. In this manner is created next to the primary chamber secondary chamber 6 with approximately (except for the volume occupied by the spindle) an equal u≤efull workin space. The secondary working space can be used as a new independent combustion chamber, or can work in cooperation with the principal chamber for the compression of the air or the expansion of the exhaust gases. Without a notable change of its total volume the machine of Fig. 4 has the double working volume as the machine of Fig. 2. The machine in Fig. with solely two oscillating parts is an "eight cylinder" engine, in whic the total volume is only about four times larger than the working volume As shown in Figures 2, 3 and 4 machines bui * Jt in accordance to this exam f oM•*. * : . _ possess a cylindrical outer form and have (like electric motors) all their moving parts εymmetricaly arranged around their rotating axis, so that they are particularly suitable for purposes (e.g. airplane motors) a iπiiiimum of vibration is desired. Example 2 Fig. 5 shows a machine in which the stroke movement of the piston 1 is caused from the crank 3 through the universal joints 3 and 4. At the sa time the piston rotates round its axis and this rotation is carried to the cylinder wall via the bolt 6, the rolls 7 and the slits 8. The aper-ture 10.regulates the inlet and outlet of the working fluid. Kejchanical energy can be given to the machine or (if it is a motor) be taken from it away through both axles 2 and 11. The important point of this construction is that the length of the pisto stroke and consequently the power of the machine depends on the relative place of the axes 2 and 11. Both axes lie on the same plane (which is t cross sectional plane in Fig- 5) . hut they can have different angles to each other. If both axes lie on the same straight line, the stroke movement of the piston disappears (piston and cylinder wall rotate with¬ out volume change). If they are displaced from the straight line, the stroke movement appears and augments when the angle between the axes increases. In Fig. 5 the axes 2 and 11 are shown in the position which cause the τπ:=-χ- * ττmιn stroke length. If the bearing 12 is turned round the axis 13 (which stays perpendicular to the plane of Fig. 5 ιthe stroke becomes - shorter until it disappears when the axes 2 and 11 are on a straight lin If the bearing 12 is turned further, the stroke appears again but with a phase difference of l8θ°.. Depending on the use of the machine this chan serves to reverse either the flow direction of the working fluid (e.g. i a circulation pump), or the rotating direction of the machine (e.g. in a compressed air motor). The motion transfer from shaft 2 to the axle 11 via the bolt 6 and the slits 8, permit the realization only of the two-stroke principle. One revolution corresnc-nds to two strokes. That makes the machine suitable for such uses as for example pumps, compressorr., hydraulic motors etc. However this motion transfer can be fulfiled also externaly through common elements (shafts, gears, chains etc). In such a case the bolt 6 does not extend outside of the piston walls, the slits 8 do not exist and the piston can have another rotation speed as the cylinder wall. Thus realizing the four-stroke (or any desired) principle. The change of the position of the bearing 12 can easily be made possibl also if the machine is in full operation, so that such a machine can continuously change its power, even reverse its working direction, durin the operation and independent of the rotation speed. These characteris constitute advantages of greatimportance for several applications: e.g. injection pumps, -vessels,or vehicles relieved from a gear box.

Claims: AMENDED CLAIMS (received by the International Bureau on 11 March 1983 (11.03.83)) 1. A piston machine with a working chamber or chambers to be used as motor and/or pump for gases and fluids and/or compressors for gases, wherein the wall and/or top of the working chamber rotates around its axis, so that one or more apertures, provided on the said wall and/or top, come during the rotation in periodical contact with a closed stationary outer part, and with inlet and outlet channels, and, optionally with additional inlet means for fluid and/or with ignition means, characterized by the fac that the working chamber (4 - 7 of Fig. 2) is cylindrical. 2. A machine according to claim 1, characterized by the ' fact that the conversion of the stroke movement of th piston (2, 3 of Fig. 2) to the rotating motion of the cylinder (1) occurs through linear (12, 13) arid curved (8, 9) guide means, wherein the linear guide means are provided on the cylinder wall, with the curved guide means being provided on the stationary outer part, or the linear guide means are provided on the stationary part, with the curved guide means being provided on the cylinder wall. 3. A machine according to claims 1 or 2,. characterized by the fact that the aperture(s) (14, 16, 20, 22 of Fig. 2) i the cylinder wall -and/or cylinder top is (are) sealed towa the stationary part through one or more rings, which are placed around said aperture(s) and pressed through self- elasticity or additional springs against the stationary pa or through rings that are placed on both sides of the aper ture(s) and extend over the periphery of the cylinder (1), the space between said rings being sealed with sealing mea disposed parallel to the cylinder axis. OMPI - - 4. A machine according to claims 1 or 2 , characterized by t fact that the sealing of the aperture(s) (14, 16, -20, 22 of Fig. 2) in the cylinder wall and/or cylinder top towards the stationary part is achieved through rings disposed within the inner wall of the stationary part and extending over the periphery thereof, the space between said rings being sealed with sealing means parallel to the cylinder axis. 5. A machine according to anyone of claims 1 to 4, characte rized by the fact that the piston is provided with at least a bolt (10, 11 of Fig. 2) engaging the linear (12, 13) and curved (8, 9) guide means surfaces in a sliding movement or through intermediate roller bearings. 6. A machine according to anyone of claims 1 to 5, characte rized by the fact that the curved guide means (8, 9 of Fig. is formed such that the piston's (2, 3) movement occurs as a function of a second or higher power in accordance with ti or as an exponential function of the time, and that an even or odd number of the piston's strokes having the same or different length or duration corresponds to one revolution of the cylinder wall. 7. A machine according to anyone of claims 1 to 6, characte- rized by the f ct that in a rotating cylinder two pistons (1, 2 of Fig. 3) having equal masses perform exactly the same symmetrical " opposite movement guided either from the same curved guide means and bolts set 90° apart, whereby the space between the pistons serves as compressor, or from different curved guide means (8, 9 of Fig. 2) whereby the pistons are shaped as double pistons (1, 2 of Fig.2) with two working surfaces, so that four chambers correspond to two pistons. OMH 8. A machine according to anyone of claims 1 to 7, characte¬ rized by the fact that the working surfaces of the pistons (1 of Fig. 4) are fixed on rods (3) which move through separating walls (4) of the cylinder, so that next to each primary working chamber (5) a secondary (6) working chamber is obtained and eight working chambers correspond to two oscillating parts, whereby the secondary chambers work inde¬ pendently or in cooperation with the primary chambers as combustion chambers, pumps or compressors. 9. A machine according to claim 1 , characterized by the fact that the conversion of the piston's (1 of Fig. 5) stroke to t rotating motion of the axle (13) occurs by means of a crank (5) and two universal joints (3, 4) , and the cylinder wall rotates together with the piston (1), guided through linear (8) grooves on said cylinder wall and a bolt (6) fixed on the piston, or rotates with another angular velocity without the connection through the linear guides and the bolt. 10. A machine according to claim 9 and including the feature of claims 3 or 4. 11. A machine according to claims 9 or 10, characterized by the fact that the position of the bearing (12 of Fig. 5) of the crank (5) relative to the cylinder (9) is variable whereby the relative position of the axis of the crank to the axis of_the cylinder, the length of the stroke, the power of the machine, and its working direction are continuou variable regardless of the rotating speed. EDITORIAL NOTE The applicant failed to renumber the amended claims in accordance with Section 205 of the Administrative Instructions. In the absence of any specific indication from the applicant as to the corres¬ pondence between original and amended claims, these claims are published as filed and as amended.

Inventors: BEKIAROGLOU PRODROMOS, BEKIAROGLOU, PRODROMOS
Applicants: BEKIAROGLOU PRODROMOS, BEKIAROGLOU, PRODROMOS
Application year: 1982
Main classification: F01B3
IPC codes: F01B3, F01B9, F01B13, F02B59, F02B75, F04B7