Title of Invention

A TWO CYCLE INTERNAL COMBUSTION ENGINE

Abstract

A two cycle internal combustion engine, comprising a plurality of engine cylinders, which are arranged in, an annular series around a common middle drive shaft and which have cylinder axes running parallel to the drive shaft, each cylinder having a pair of pistons movable towards and away from each other and a common, intermediate working chamber for each pair of pistons, while each piston is provided with its axially movable piston rod, the free outer end of which forms via a support roller a support against its curve shaped, that is to say "sine" -curve shaped, cam guide device, which is arranged at each of opposite ends of the cylinder and which controls movements of the piston relative to the associated cylinder, characterized in that the two pistons in each cylinder have mutually differing piston phases, which are controlled by mutually differing cam guide devices, the cam guide devices being designed with equivalent mutually differing "sine" -planes ( "sine" - curves).

Full Text

The present invention relates to an arrangement in a two cycle combustion engine with internal combustion, comprising a plurality of engine cylinders, which are arranged in an annular series around a common central drive shaft and which have cylinder axes running parallel to the drive shaft, each cylinder including a pair of pistons movable towards and away from each other and for each pair of pistons a common, intermediate work chamber, while each piston is equipped with its axially movable piston rod, the free outer end of which forms via a support roller a support against its curve-shaped, that is to say "sine"-curve shaped, cam guide device, which is arranged at each of opposite ends of the cylinder and which guides movements of the piston relative to the associated cylinder. Geometric considerations of the afore-mentioned motor system When the drive shaft of the engine is moved in a circular path, the oscillation movements of the engine pistons can correspondingly according to the afore¬mentioned motor system be observed graphically as to time in a sine--shaped curve path according to Formula 1 : y = sine x. By the use of a sine curve-shaped cam guide device the backwards and forwards piston movements of the individual pistons of the cylinders can in fact be controlled, so that the oscillation movements of the pistons synchronously coincide with the rotational movement of the drive shaft. Over the course of a complete rotation of the drive shaft, the pistons are moved backwards and forwards in a forcibly controlled"manner in one or more working strokes, which are accurately synchronised with the rotational movement of the drive shaft. In other words the rotational movement of the cam guide device and the drive shaft will be directly connected to the oscillation movement of the pistons, and vice - versa The backwards and forwards movements of the pistons will correspondingly constitute a multiple of the rotary movement of the drive shaft with each 3 60° rotation of the drive shaft. In other words each piston will move backwards and forwards in the associated cylinder a total number of times, that is to say from one to for example four times with each 360° rotation of the drive shaft. Owing to the cam guide device, which controls the oscillating movements of the pistons in an associated cylinder, being rotated synchronously with the drive shaft of the engine, the oscillation movements of the pistons can consequently be controlled by designing the cam guide device with a sine-shaped curve contour, so that these conform to the rotational movement of the drive shaft. "Sine" - concept. When the term "sine" is employed herein in connection with expressions, such as "sine" - concept, "sine" -curve, "sine" - plane, etc.), a curve contour is expressed which does not constitute a mathematical sine contour according to the formula 1 above, but on the other hand expresses a varying curve contour, which only generally resembles the path of a mathematical sine contour. By the term "sine" - contour there shall be designated generally herein a sine-like contour. According to the invention the aim is, in certain constructional connections, with regard to designing the cam guiae aevice witn a particular curve contour which in different ways deviates from a mathematical sine contour. Generally this means further, according to the invention, that by designing the cam guide device with a specially fashioned "sine" contour, which deviates from a conventionally known "sine" contour, the piston movements can be adapted in a corresponding manner to additional engine functions relative to the rotational movement of the drive shaft and relative to previously proposed solutions. According to the invention the general aim is to design the cam guide device so that there is a possibility of achieving optimum operating conditions for pistons of the motor, based on a simple and operatively reliable operating sequence. When one speaks herein about "sine" - plane, there is meant the local part of the cam guide device, which has a "sine" - curve contour. In practice the individual cam guide device has a 3 60° arcuate contour, which corresponds to a multiple of such said "sine" - planes. Combustion engines, where the axial movement of the pistons is individually controlled by a cam guide device via associated "sine" - planes, function generally accord¬ing to the so-called "sine" - concept, which has been known for a number of years. Originally the "sine" - plane has had a contour, which resembles to a large degree the mathematical sine contour, that is to say with mutually symmetrical and uniformly curved curve portions. According to the patent literature, curve contours have gradually been proposed which in different ways deviate from the mathematical sine contour. This is also typical of the curve-contour of the cam guide devices according to the present invention. According to the "sine" - concept the mechanical energy is transferred from the single piston to the common drive shaft of the engine cylinder, that is to say via a support roller of an associated piston rod to the "sine" -plane of the cam guide device. The "sine" - planes, which separately control the oscillation movements of the pistons, transfer during the oscillation movements of the pistons: - partly kinetic energy from the expansion stroke of the pistons via the "sine" - plane to the drive shaft, so as to subject the drive shaft to a rotary movement with associated torque, and - partly torsional moments from the drive shaft via the "sine" - plane back to the pistons, so as to subject the pistons to the necessary kinetic energy during the compression stroke. In combustion engines of the kind indicated by way of introduction the pistons are moved axially backwards and forwards in associated cylinders, almost exclusively in rectilinear movements axially along the drive shaft, while the piston rods and associated support rollers are moved in corresponding rectilinear movements and consequently transfer motive forces from the support rollers to the associated "sine" - plane in an axial direction along the drive shaft. The transfer of the motive forces from the pistons via support rollers to the "sine" - plane, which is designed in driving connection with the drive shaft, and return forces which are transferred in the opposite direction from the drive shaft to the pistons via the "sine" - plane, occur on curve portions which extend obliquely of the rotational plane of the drive shaft. In other words motive forces are transferred between the support rollers and the "sine" - plane during displacement of the support rollers axially along the drive shaft. In the dead points between the backwards and forwards going piston stroke there occurs however no transfer of motive forces, this despite that in the one dead point, that is to say at the close of the compression stroke and after ignition of injected fuel, significant motive forces arise between the pistons going towards and away from each other. With the present invention the particular aim is to utilise the last-mentioned condition in connection with a special design of the cam guide device, so that in said dead point a hitherto disregarded possibility can be achieved for controlling the combustion process of the engine in an especially favourable manner. Comparison of four stroke and two stroke engines In a four stroke combustion engine the piston rods transfer their motive forces via the "sine" - plane in the respective four strokes, that is to say - with minimal forces in the air suction stroke, - with substantially greater forces in the compression stroke, - with the largest forces in the expansion stroke and - with minimal forces in the exhaust ejection stroke. In a two stroke - combustion engine the piston rods transfer their motive forces via the "sine" plane in the respective two strokes, that is to say - with relatively small forces in a combined air injection and compression stroke and - with substantially greater forces in a combined expansion and exhaust ejection stroke. However it is also usual to allow air suction/air injection and exhaust ejection to occur more or less in parallel at the end of the combined expansion and exhaust ejection stroke and at the beginning of the combined air injection and compression stroke. Four stroke engines have hitherto generally had a dominating use on the market, relative to the two stroke engine, within many different fields of application (by way of example for petrol engines for private cars). As a result of the operating strokes of the four stroke motor being distributed over four piston strokes, there is a greater prospect of adapting the individual functions of the single strokes in a simpler manner than in a two stroke engine, where all the current functions must be adapted over two strokes. The functions of the two stroke engine are necessari¬ly more compact and thereby also more complicated, than in i four stroke engines. Four stroke engines have hitherto also been simpler to adapt with the "sine" - concept than two stroke engines. On the other hand two stroke engines have various other advantages over four stroke engines, precisely as a consequence of a fewer number of operating strokes. With the present invention the aim is inter alia to solve the problems one has hitherto had with two stroke engines in connection with the application of the "sine" -concept. According to the invention the aim is to design the cam guide device in a particular manner, so that the "sine" - concept can be utilised in two stroke engines under correspondingly favourable or under still better operating conditions than in four stroke engines. Historic development of the "sine" - concept: A four stroke combustion engine is known from for example US 1 352 985 (1918) having a single cam guide device. The cam guide device is based on a sole, common cam control for a sole, annular series of pistons in each of their associated separate engine cylinders. Each and all the cylinders are correspondingly arranged in a sole, annular series around the drive shaft of the engine. The piston rods are separately shored up via their respective support rolls in the common cam guide device. From US 1 802 902 (1929) for instance a four stroke combustion engine is known having a corresponding single cam guide device. In this case, instead of just one series of pistons, there are employed two series of pistons axially separated, but mutually directly coupled together. The pistons are arranged in tandem in their respective axially oppositely facing cylinders, that is to say the cylinders and the pistons are placed aligned in pairs, axially opposite each other. The pistons are furthermore rigidly connected to each other via a common piston rod and have their respective piston heads turned away from each other at axially opposite ends of the engine each towards its respective working chamber in its respective associated cylinder. The pistons cooperate in pairs with just one, common cam guide device. The common piston rod of each pair of pistons is provided in a middle region between the shirt portions of the pistons with a common support roller, which is supported and is controlled in a common, sole cam guide device for all the pistons. More specifically a centrally arranged cam guide device is employed with a double-sided arrangement of mutually opposite "sine" - planes following in series, which cooperate with a single series of support rollers. The afore-mentioned placing of the cam guide device and the support rollers centrally between two series of mutually opposite pistons, where there is employed a single series of support rollers in a common, double-sided cam guide device, gives little possibility of deviating contours in the two cooperating series of oppositely facing "sine" - planes, since the contours of the "sine" -planes are necessarily adapted after the opposite working phase of the respective two oppositely facing pistons of the pair of pistons. From US 5 031 581 (1989) for instance a four stroke combustion engine is known having two separate cam guide devices. Each cam guide device, which cooperates with its respective set of pistons and with its respective associated set of support rollers, is individually designed corresponding to the construction according to US 1 352 985. According to US 5 031 581 the cylinders are arranged in a single group of cylinders, that is to say the cylinders are arranged in an annular single series around the drive shaft. The pistons, which are received in pairs in a respective one of the cylinders, are served by two separate cam guide devices, that is to say the one piston of each pair of pistons is controlled by a first cam guide device, while the remaining piston is controlled by a second cam guide device. Each cylinder is consequently equipped with separate pistons movable in pairs towards and away from each other each with its separate~piston rod, which cooperates individually via an associated support roller with a respective one of two opposite cam guide devices with associated "sine" - planes. The cam guide devices of the two axially distinct groups of pistons are arranged axially endwise outside respective ends of the engine. The piston heads of said pairs of pistons face mutually towards each other in a common working chamber of the associated cylinder, that is to say towards a common working chamber, which is arranged midway between said pair of pistons. In GB 2 019 487 a four cylinder two scroke engine is shown with a pair of pistons going towards and away from each other in each of said four cylinders. An arrangement is employed where the ignition occurs simultaneously in two of the four cylinders, that is to say in pairs of alternate cylinders. In the patent specification it is indicated that the contour of the cam can be designed so that the pistons can be moved in a most favourable manner in connection with expansion of the combustion product. There is employed a desired level or steady contour for emptying or scavenging of exhaust before new fuel is introduced into the cylinder. In the drawings there is shown, in each of two mutually opposite cam grooves, a more or less rectilinear, local cam contour in mutual turning points lying directly opposite each other forming "sine" - curve portions. More specifically the rectilinear cam contour is illustrated in only the one of two succeeding, turning points of the "sine"-curve forming "sine"-curve portions, namely where the respective pistons occupy one after the other their most remote outer positions with exhaust and scavenging ports open to the maximum. Present Invention. The present invention, which relates to two cycle engines, takes its starting point as to arrangement in a four cycle engine with piston and cylinder arrangement according to the afore-mentioned US 5 031 581. In particular the aim according to the invention is to be able to adapt the "sine" - concept to a two stroke engine, so that at least equally favourable and preferably still more favourable operating conditions can be achieved than what are attained in the four stroke engine according to US 5 031 581. In a four cycle engine four respective strokes (air injection stroke, compression stroke, expansion stroke and exhaust rejection stroke) are employed one after the other, so that the different engine functions can be accommodated in each stroke, while in a two cycle engine the exhaust rejection and air injection take place in the transition zone between the expansion stroke and the compression stroke, that is to say in direct connection with remaining engine functions in each working sequence. With a two cycle engine different functions of the two oppositely directed cycles must consequently be combined. According to the present invention the aim is also to combine the various engine functions in a two cycle engine in an especially favourable manner, in a particular design of the "sine" - plane of the pistons, such as will be described in more detail below. Inter alia the aim is, correspondingly as shown in a two cycle engine according to GB 2 019 4 87, to employ a more or less rectilinear contour in the turning point-forming "sine"-curve portions where the pistons assume their most remote outer position with exhaust and scaveng¬ing ports open to the maximum. According to the invention is employed the following combination: - that the "sine" - plane does not need to have a curve contour, which lies as closely or tightest possible up to, but on the contrary can depart to a significant degree from a "sine" - contour and from previously known "sine" - contours, and - that the cam guide devices can be designed with "sine" - planes, which can vary to a significant degree mutually from each other, while in addition an especially favourable engine solution can be achieved totally. The arrangement according to the invention is characterised in that the two pistons in each cylinder have mutually differing piston phases, which are controlled by cam guide devices designed mutually differently, the cam guide devices being designed with equivalent mutually differing "sine" - planes. In other words with such separate, mutually differing cam control of the pistons of each pair of pistons there can be achieved an especially favourable control and thereby favourable accommodation of the different working functions, which are to be performed in a two cycle engine. Thereby one can ensure according to the invention movement of the pistons of the pair of pistons in a mutually differing manner, but nevertheless achieve favourable collective working conditions in a common working chamber between piston heads of the pair of pistons. Phase displacement of the cam guide devices. A practical, especially favourable solution according to the invention is characterised in that the respective cam guide devices of the two pistons, are phase-displaced relative to each other, at any rate in certain portions of the "sine" - plane. According to a first aspect of the invention a favourable, separate control of the scavenging air ports can inter alia be obtained hereby via the cam guide device of the one piston and a correspondingly favourable, separate control of the exhaust ports via the cam guide device of the other piston. Consequently for instance, by such phase displacement, the opening and closing of the scavenger ports and the exhaust ports at various points in time can be achieved and these points in time can be determined by equivalent designing of the individual cam guide device. Stated in another manner the two pistons can separately open and close associated ports (exhaust ports/scavenger air ports) , while the respective piston occupies a corresponding axial position in the associated cylinder, but by virtue of the mutual phase displacement between the piston movements, the opening and closing of the various ports can take place correspondingly phase-displaced. Special design of the "sine" - plane According to another aspect of the present invention one can have the possibility in remaining portions of the "sine" - plane of employing more or less coinciding, that is to say non-phase-displaced portions, by limiting the phase displacement to certain portions of the "sine" -plane. This has significance for the remaining engine functions. In this connection a characterising feature is that at least one piston of the cylinder, and preferably both pistons of the cylinder, are held separately, axially stationary or largely stationary, in a portion of the working chamber at the dead point between the compression stroke and the expansion stroke, controlled by an equivalent rectilinear or largely rectilinear portion of the associated "sine" - plane. By designing said "sine" - plane portion rectilinearly or largely rectilinearly in a plane at right angles to the driving axis of the engine, a hitherto disregarded possibility is obtained for creating especially favourable working conditions during the combustion phase of the fuel. According to the invention it will in fact be possible to define in the working chamber a particular combustion chamber corresponding to said working chamber portion by means of a particular design of the "sine" - plane. This combustion chamber can consequently have a constant or approximately constant volume over a relatively large arcuate length of the longitudinal dimension of the "sine" - plane and of the rotational arc of the drive shaft. In other words it can be ensured according to the invention that said combustion chamber has a constant or largely constant volume over a sufficiently large arcuate length so that large portions, for instance the whole or largely the whole of the combustion process can take place in said combustion chamber. When it is indicated herein that the combustion chamber can have a constant or largely constant volume this has a connection with the detailed design of the "sine" - plane at the dead point between the compression stroke and the expansion stroke. In other words with an accurate rectilinear portion in the "sine" - plane corresponding constant volumes can be obtained, while with a more or less rectilinear portion equivalent largely constant volumes can be obtained. This involves being able to adapt the contour of the "sine" -plane according to practical conditions in different cases of application. In practice partly rectilinear "sine" - plane portions and partly preceding and subsequent, largely rectilinear "sine" - plane portions can be employed. By the afore-mentioned solution, which is based on a combustion chamber with a constant or largely constant volume in a dead portion at the transition from compression stroke to expansion stroke, one has firstly a chance of utilising the energy collected which is generated in the combustion process and having full power even at the beginning of the expansion phase. Consequently said energy can be utilised with full effect immediately the respective piston has moved itself past its dead point or its dead portion. This discharge of energy can thereby be used at full strength already in said curved transition portion where the piston accelerates from the stationary to optimal piston movement and can thereafter continue at great strength in the following expansion phase. Secondly, with such a combustion chamber having constant volume, one has the possibility of obtaining a more favourable combustion of the fuel, that is to say combustion of larger portions of the fuel, even before the expansion phase starts. This can be ensured by providing that considerable portions of the fuel are consumed in the combustion chamber in or just at said dead portion. In addition a better utilisation of the energy of the fuel is obtained viewed totally, by being able to ensure that a higher portion of the fuel by way of percentage is consumed in the working chamber before exhaust gases are discharged from the working chamber at the close of the expansion stroke. In other words there is the possibility according to the invention of increasing the output of the engine to a significant degree relative to previously known solutions. According to the invention there is consequently obtained a generally greater engine output. In addition the escape of CO gas, NOX gas, and the like is reduced, and thereby a better environmental combustion is also obtained. There must also be mentioned that after-combustion of the fuel, which occurs in the expansion stroke per se and which to a large degree can compensate for the volume enlargement in that portion of the working chamber where oscillation movements of the pistons take place, can be carried out according to the invention in a controlled manner in good time before the exhaust ports open, that is to say gradually as the expansion stroke propagates itself in the working chamber. In other words one has a chance to distribute the motive power in an advantageous manner from the beginning of the expansion stroke and further through considerable portions of the expansion stroke before the exhaust ports open, even with an optimal combustion already before the expansion stroke. The energy which is discharged, by the released possibility of movement of the pistons from the stationary condition, can consequently be discharged relatively momentarily and at full strength from a combustion chamber having a constant volume. The discharge itself can occur in an accelerating manner via a curved "sine" - plane portion, which constitutes the transition portion between said rectilinear dead portion and a subsequent rectilinear expansion portion. In the subsequent rectilinear expansion portion, the expansion takes place linearly, that is to say in a working chamber having roughly speaking a linear increasing volume. Illustration by drawings: Further features of the present invention will be evident from the following description having regard to the accompanying drawings, which show some practical embodiments and in which: Fig. 1 shows a vertical section of an engine according to the invention. Fig. la and lb show in a corresponding segment of Fig. 1 vital parts of the engine and illustrate in Fig. la pistons of the engine in a position with maximum mutual spacing and in Fig. lb pistons of the engine in a position with minimal mutual spacing. Fig. 2 shows schematically a first cross-section illustrated at one end of the cylinder of the engine in which there is shown a scavenging air intake. Fig. 3 shows schematically a second cross-section illustrated at the other end of the cylinder of the engine, in which there is shown an exhaust outlet. Fig. 4a shows schematically in a third cross-section, the middle portion of the engine cylinder, where the fuel is supplied and the ignition of the fuel occurs, illustrated in a first embodiment. Fig. 4b shows in a cross-section, which corresponds to Fig. 4a, the middle portion of the cylinder according to a second embodiment. Fig. 5a shows in longitudinal section a segment of the engine according to Fig. lb. Fig. 5b shows a cam guide device with associated drive shaft, illustrated in longitudinal section with a segment of the engine according to Fig. lb. Fig. 5c shows a cross head in side view. Fig. 5d and 5e show the cross head according to Fig. 5c seen respectively from above and below. Fig. 5f shows the piston rod seen in side view. Fig. 5g shows the piston rod according to Fig. 5f seen from above. Fig. 5h shows a piston according to the invention in vertical section. Fig. 6-8 show schematically illustrated and spread in the plane of the drawing a general pattern of movement for a first of two pistons associated with each cylinder, used in connection with a three cylinder engine, and illustrated in different angular positions relative to the rotary movement of the drive shaft. Fig. 6a shows schematically the principle for transferring motive forces between the roller of the piston rod and an associated obliquely extending portion of a "sine" - plane. Fig. 9 shows schematically illustrated and spread in the plane of the drawing a more detailed pattern of movement for two pistons of each cylinder, illustrated in different angular positions relative to the rotary movement of the drive shaft, illustrated in connection with a five cylinder engine. Fig. 10 shows in a representation corresponding to Fig. 9, the pistons in respective positions relative to associated cylinders, in a subsequent working position. Fig. 11 shows schematically a segment of a central portion of a "sine" - plan for two associated pistons of each cylinder. Fig. 12 shows a detailed curve contour for a "sine" -plane for a first piston in each cylinder. Fig. 13 shows a corresponding detailed curve contour for a "sine" - plan for a second piston in each cylinder. Fig. 14 shows a comparative compilation of the curve contours according to Fig. 12 and 13. Fig. 15 shows in section and in longitudinal section an alternative construction of a cam guide device with associated pressure rollers arranged at the outer end of a piston rod. Fig. 16 shows the same alternative solution, as illustrated in Fig. 15, shown in section in a direction radially outwards from the cam guide device. Fig. 17 and 18 show in elevation and in horizontal section respectively the guiding of the head portion of the piston rod along a pair of control bars extending mutually in parallel. In connection with Fig. 1 reference herein shall generally be made to a two cycle combustion engine 10 having internal combustion. Especially there will be described such an engine 10 adapted according to a so-called "sine" concept. In Fig. 1 there is specifically shown a combustion engine 10 according to the invention illustrated in cross-section and in a schematic manner. According to the invention the aim according to a first aspect of the invention is combustion in a specially defined combustion chamber Kl (see Fig. lb), as will be described in more detail below. Furthennore according to a second aspect according to the invention the aim is a favourable control of opening and closing exhaust ports 25 and scavenging ports 24, as will be described further below. In the embodiment illustrated in Fig. 1 there is shown a drive shaft 11 in the form of a pipe stump, which passes axially and centrally through the engine 10. The drive shaft 11 is provided at its illustrated one end with a radially outwardly projecting, first head portion 12a, which forms a first cam guide device, at its other illustrated end the drive shaft 11 is provided with an equivalent radially outwardly projecting, second head portion 12b, which forms a second cam guide device. The head portions/ the cam guide devices 12a, 12b in the illustrated embodiment are represented separately and are connected separately to the drive shaft 11 each with their fastening means. The cam guide device 12a surrounds the drive shaft 11 at its one end 11a and forms an end support against end surface lib of the drive shaft 11 via a fastening flange 12a" and is stationarily secured to the drive shaft via fastening screws 12a"". The cam guide device 12b surrounds a thickened portion lie of the drive shaft 11 at its opposite end portion lid. The cam guide device 12b is not, as is the cam guide device 12a directly secured to the drive shaft 11, but is on the other hand arranged axially displaceable a limited extent axially along the drive shaft 11, especially with the idea of being able to regulate the compression ratio in cylinders 21 of the engine 10 (only the one of a number of cylinders is shown in Fig. 1). End portion lid (see Fig. 1 and 5a) of the drive shaft 11 forms a radially offset sleeve portion to which there is fastened cup-shaped carrying member 13. The carrying member 13 is provided with a fastening flange 13" which with fastening screws 13"" is secured to end portion lid of the drive shaft 11. Between upper end surface 13a of the carrying member 13 and an opposite shoulder surface lie of the drive shaft 11 there is defined a pressure oil chamber 13b. In the pressure oil chamber 13b there is slidably received a compression simulator 12b" in the form of a piston-forming guide flange, which projects from the inner side of the cam guide device radially inwards into the pressure oil chamber 13b for sliding abutment against the outer surface of the end portion lid. In order to prevent mutual turning between the cam guide device 12b and the carrying member 13 and the drive shaft 11 the guide flange 12b" is passed through by a series of guide pins 12" which are anchored in their respective bores in the end surface 13a of the carrying member 13 and in the shoulder surface lie of the drive shaft 11. The pressure oil chamber 13b is supplied pressure oil and is drained of pressure oil via transverse ducts llf and llg through end portion lid of the drive shaft 11. An oil guide means 14, which is put axially inwards into mutually aligned axial bores in the end portion lid of the drive shaft 11 and in fastening flange 13" of the carrying member 13, provides for pressure oil and return oil to be led to and from the ducts llf and llg via separate guide ducts 14a and 14b and adjacent annular grooves 14a" and 14b" in the oil guide means 14. Control of pressure oil and return oil to an from the pressure oil chamber 13b on opposite sides of the compression simulator 12b" of the cam guide device 12b takes place from a remotely disposed commercially conventional control arrangement, not shown further, in a manner not shown further. The drive shaft 11 is, as shown in Fig. 1, connected at opposite ends to equivalent drive shaft sleeves 15a and 15b. The sleeve 15a is fastened with fastening screws 15a" to the cam guide device 12a, while the sleeve 15b is fastened with fastening screws 15b" to the carrying member 13. The sleeves 15a and 15b are rotatably mounted in a respective one of two opposite main support bearings 16a,16b, which are fastened at opposite ends of the engine 10 in a respective end cover 17a and 17b. As shown in Fig. 1, the end covers 17a and 17b are correspondingly fastened to an intermediate engine block 17 by means of fastening screws 17". Internally in the engine 10 a first lubricating oil chainber 17c is defined between the end cover 17a and the engine block 17 and a second lubricating oil chamber 17d between the end cover 17b and the engine block 17. There is shown an extra cap 17e attached to the end cover 17b and an external oil conduit 17f between the lubricating oil chamber 17c and the oil cap 17e. Further there is illustrated a suction strainer 17g connected to a lubri¬cating oil conduit 17h which forms a communication between the lubricating oil chamber 17d and an external lubricat¬ing oil arrangement (not shown further). The oil guide means 14 is provided with a cover-forming head portion 14c which is fastened to end cover 17b of the engine 10 with fastening screws 14c". The cover-forming head portion 14c forms a sealing off relative to the lubricating oil chamber 17c endwise outside the support bearing 16b. Correspondingly there is fastened to the end cover 17a endwise outside the support bearing 16a a sealing cover 14d with associated sealing ring 14e. The engine 10 is consequently generally constructed of a driven component, that is to say a rotatable component, and a driving component, that is to say a non-rotating component. The driven component comprises drive shaft 11 of the engine and carrying member 13 of the drive shaft and drive shaft sleeves 15a,15b plus the cam guide devices 12a and 12b, which are connected to the drive shaft 11. The driving, non-rotating component comprises cylinders 21 of the engine with associated pistons 44,45. According to the present invention there is ensured a regulation of the compression ratio of the engine by 5ffecting a regulation internally, that is to say mutually :)etween the parts of the driven component. More specifically the one cam guide device 12b is displaced ixially backwards and forwards relative to the drive shaft .1, that is to say within the defined movement space in said pressure oil chamber 13a, which is determined by the guide flange 12b" and the part-chambers of the oil chamber 13a on opposite sides of the guide flange 12b". In practice it is a question of a regulation length of some few millimetres for smaller motors and of some centimetres for larger engines. The respective volume differences of the associated working chambers have however equivalent compression effects in the different engines. For instance a stepwise or stepless regulation of the compression ratios can be considered according to need, for example adapted with graduated control of the cam guide device 12b to respective positions relative to the drive shaft 11. The control can for example occur automatically by means of electronics known per se, based on different temperature sensing equipment, and the like. Alternatively the control can occur by manual control via suitable regulation means, which are not shown further herein. By effecting the regulation of the cam guide device 12b in connection with the driven component of the engine, one avoids influence on the general control of the arrangement of associated piston 44, piston rod 48, main support wheel 53 and auxiliary wheel 55, that is to say influence on the mechanical connection between the driving component and the driven component is avoided. On the other hand, with such a regulation of the cam guide device 12b, there is obtained an axial regulation internally in the driving component, in such a way that the arrangement of piston 44, piston rod 48, main support wheel 53 and auxiliary wheel 55 can be displaced collectively via the cam guide device 12b relative to the associated cylinder 21, independently of the concrete compression regulation in practice. In Fig. 1 and lb there is indicated by a broken line a centre space 44" between the piston heads of the pistons 44,45 at a normal compression ratio when the cam guide device 12b occupies the position illustrated in Fig. 1. By the full line there is indicated a centre space 44"" between the piston heads of the pistons 44,45 when guide flange 12b" of the cam guide device 12b is pushed to the maximum upwardly against the shoulder surface lie of the piston rod 11. The engine 10 is shown divided up into three stationary main components, that is to say a middle member, which constitutes the engine block 17 and two cover-forming housing members 17a,17b which are arranged at a respective one of the ends of the engine 10. The housing members 17b, 17c are consequently adapted to cover their respective cam guide devices 12a,12b, support wheels 53 and 55 and their associated bearings in respective piston rods 4 8,49 at their respective end of the engine block 17. All the driving and driven components of the engine are consequently effectively enclosed in the engine 10 and received in an oil bath in the associated lubricating oil chambers 17c and 17d. In the engine block 17 in the illustrated embodiment, there is used in connection with a three cylinder engine, correspondingly designed with three peripherally separated engine cylinders 21. Only the one of the three cylinders 21 is shown in Fig. 1, la and lb. The three cylinders 21, which are placed around the drive shaft 11 with a mutual angular spacing of 12 0°, are designed according to the illustrated embodiment as separate cylinder-forming insert members, which are pushed into an associated bore in the engine block 17. In each cylinder/ cylinder member 21 there is inserted a sleeve-shaped cylinder bushing 23. In the bushing 23 there is designed, as shown further in Fig. la and lb (see also Fig. 2 and 3), an annular series of scavenging ports 24 at one end of the bushing 2 3 and an annular series of exhaust ports 25 at the other end of the bushing 23. Equivalently in wall 21a of the cylinder 21 there are arranged scavenging ports 26, which are radially aligned with scavenging ports 24 of the bushing 23, as is shown in Fig. 2, while exhaust ports 27, which are radially aligned with exhaust ports 25 of the bushing 23, are equivalently designed in the cylinder wall 21a, as is shown in Fig. 3. In Fig. 1 there is shown an annular inlet duct 28 for scavenging air, which surrounds the scavenging ports 26, and a scavenging air intake 29 lying radially outside. As is shown in Fig. 2 the scavenging air ducts 28 extend at a significant oblique angle u relative to a radial plane A through the cylinder axis, specially adapted to put the scavenging air in a rotational path 3 8 internally in the cylinder 21, as is shown by an arrow B in Fig. 2. There is further shown in Fig. 1 an annular exhaust outlet duct 30, which surrounds the exhaust ports 27, plus an exhaust outlet 31 emptying radially outwards. In Fig. 3 there is shown an equivalent oblique run of the exhaust ports 27 at an angle v relative to the radial plane A through the cylinder axis, specially adapted to lead the exhaust gases from the rotational path 38 internally in the cylinder in an equivalent rotational path outwards from the cylinder 21, as is shown by an arrow C. The exhaust ports 2 7 are shown opening radially outwards to facilitate the outward flow of the exhaust gas from the cylinder 21 outwards towards the exhaust outlet duct 30. In the conventionally known manner the scavenging air is used to push out exhaust gas from a preceding combustion phase in the cylinder, in addition to supplying fresh air for a subsequent combustion process in the cylinder. In this connection there is employed according to the invention in a manner known per se a rotating air mass as shown by arrows 3 8 (see Fig. la and 4a) in working chamber K of the cylinder 21 in the compression stroke. In Fig. la,lb and 4a there is shown a fuel injector or nozzle 32 received in a cavity 33 in the cylinder wall 21a. The injector/nozzle 32 has a pointed end 32" (see Fig. 4a) projecting through a bore 34 in the cylinder wall 21a. The bore 34 passes through the cylinder wall 21a at an oblique angle, which is not marked further in Fig. 4a, but which corresponds to the angle u, as shown in Fig. 2. The pointed end 32" projects further through a bore 3 5 in the bushing 23, in alignment with the bore 34. Mouth 36 (see Fig. 4a) of the nozzle/injector 32 is arranged so that a jet 3 7 of fuel can be directed, as is shown in Fig. 4a, obliquely inwards in a rotating mass of air as shown by the arrows 3 8 in cylinder 21, just in front of a spark plug 3 9 (possibly ignition pin) arranged in a chamber zone which forms a part of the combustion chamber Kl (see Fig. lb) . In Fig. 4b there is shown an alternative construction of the solution as shown in Fig. 4a, there being employed in addition to a first fuel nozzle 32 and a first ignition arrangement 39 a second fuel nozzle 32a and a second ignition arrangement 39a in one and the same disc-formed combustion chamber Kl. Both the nozzles 32 and 32a are designed correspondingly as described with reference to Fig. 4a and both the ignition arrangements 3 9 and 3 9a are corresponding as described with reference to Fig. 4a. In the nozzle 32a the associated components are designated with the reference designation "a" in addition. In the illustrated embodiment of Fig. 4b the nozzles 32,32a are shown mutually displaced an angular arc of 180°, while the ignition arrangements 39,39a are correspondingly shown mutually displaced an angular arc of 180°. In practice the relative spacings can be altered as required, that is to say with different mutual spacings, for instance depending upon the point in time of the mutual ignition, and the like. Further there is indicated in Fig. 1 a cooling water system for general cooling of the cylinder 21. The cooling water system comprises a cooling water intake not shown further having a first annular cooling water duct 41 and a second annular cooling water duct 42. The ducts 41,42 are mutually connected via an annular series of axially extending connecting ducts 43 (see Fig. 3). The axially extending ducts 43 pass through the cylinder wall 21a in each intermediate zone 2 7a between the exhaust ports 27, so that these zones 27a especially can be prevenited from superheating by being subjected locally to a flowing through of cooling medium. The discharge of cooling water, which is not shown further in Fig. 1, is connected to the cooling water duct 42 remote from the cooling water intake, in a manner not shown further. Internally in the bushing 23 there are two axially movable pistons 44,45 movable towards and away from each other. Just by the respective top 44a,45a of the piston and by the skirt edge 44b,45b of the piston there is arranged a set of piston fourths 46 in a manner known per se. The pistons 44,45 are movable synchronously towards and away from each other in a two cycle engine system. Further details of the pistons are shown in Fig. 5h. The piston 44 is shown in the form of a relatively thin-walled cap having top portion 44a and skirt portion 44b. Innermost in the internal hollow space of the piston there is arranged a support disc 44c, thereafter follows a head member 48c for an associated piston rod 48, a support ring 44d and a clamping ring 44e. The head member 4 8c is provided with a convexly rounded top surface 48c" and concavely rounded off bottom surface 48c"", while the support disc 44c is designed with an equivalent concavely rounded upper support surface 44c" and the support ring 44d is provided with a convexly rounded lower support surface 44d". The head member 48c is consequently adapted to be tilted about a theoretical axis relative to the piston controlled by the support surfaces 44c" and 44d". By abutment against a shoulder portion 44f internally in the piston the ring 44e provides for the head member 4 8c - and thereby the piston rod 4 8 - having a certain degree of fit and thereby a certain possibility of turning about said theoretical axis of the piston 44 during operation. The head member 48c is provided with a middle, sleeve-shaped carrying portion 48g having rib portions 48g" projecting laterally outwards which form a locking engagement with equivalent cavities (not shown further) internally in the associated piston rod 48 (see Fig. la and lb). In Fig. la the pistons 44,45 are shown in their equivalent, one outer position. This outer position, where there is a maximum spacing between the pistons 44,45, is designated herein generally as a dead point Oa for the piston 44 and Ob for the piston 45. In the said dead point positions Oa and Ob the piston 44 uncovers the scavenging ports 24, while the piston 45 uncovers the exhaust ports 25, opening and closing of the scavenging ports 24 being controlled by positions of the piston 45 in the associated cylinder 21, while opening and closing of the exhaust ports 25 is controlled by positions of the piston 44 in the associated cylinder 21. This control will be described in more detail in what follows having regard to Fig. 12-14. In addition this control will be described with additional effects having regard to the afore-mentioned regulation of the cam guide device 12b along the drive shaft 11. When the pistons 44,45 occupy their opposite outer positions, where there is a minimal spacing between, as is shown in Fig. lb, these positions are usually designated as dead point positions. However according to the present invention the pistons 44,45 are stationary, that is to say without or broadly speaking without axial movement relative to each other in and at these dead point positions. In that the pistons are held stationary not only in the dead point position, but also in adjacent portions of the respective "sine" - plane, as will be described further below, a volumetrically more or less constant working chamber (combustion chamber) over a certain arcuate length can be ensured, that is to say over a considerably longer portion of the "sine" - plane than known hitherto. Consequently the pistons 44,45 are at rest or broadly speaking at rest over a portion of the "sine" -"plane, which is designated herein as a "dead portion" 4a for the piston 44 and as a "dead portion" 4b for the piston 45. Such dead portions 4a and 4b are further illustrated in Fig. 12 and 13. In said dead portions there is defined in the working chamber K a so-called "dead space", which herein (for reasons which will be evident from what follows) is designated as the combustion chamber Kl. The combustion chamber Kl is according to the invention mainly defined in and at a transition portion between the compression phase and expansion phase of the two cycle engine, as will be described in more detail in what follows. During the expansion phase, that is to say from the position of the piston as shown in Fig. lb to the position of the piston as shown in Fig. la, the working chamber K is expanded from a minimum volume, shown by the combustion chamber Kl, gradually to a maximum volume, as shown in Fig. la and at said dead point Oa and Ob in Fig. 9 and 10, the combustion chamber Kl being gradually expanded with another chamber K2 in which the expansion and compression strokes of the pistons 44,45 take place. According to the invention the combustion chamber Kl is defined to a considerable degree in said dead portion/dead space. In practice however the combustion can also continue a bit just outside said dead space, something which will be explained in more detail below. In connection with the change of the compression ratio in the working chamber there can be a question in the position as shown in Fig. 10 about different volumes in the combustion chamber Kl all according to which regulation is effected during use of the engine. From the above there should in that case also be a question about different volumes in the combustion chamber in the opposite position as shown in Fig. la. However one must be aware of the piston strokes for the individual piston 44,45 being precisely equally long under all operative conditions, regardless of the compression ratio which must be employed. Each piston 44,45 is rigidly connected to its respective pipe-shaped piston rod 48 and 49, which is guided in a rectilinear movement via a so-called cross-head control 50. The cross-head control 50 is arranged partly in the engine block 17 and partly in the respective cover member 17a and 17b at the equivalent free outer end of the respective piston rod 4 8,49. The cross-head control 50, which is shown in detail in Fig. 5a, forms an axial guide for the piston rod 48 and 49 just within and just outside the engine block 17. With reference to Fig. 5a there is a rotary pin 51 which is fastened at one end of the pipe-shaped piston rod 48 and which passes through the piston rod 48 crosswise, that is to say through its pipe hollow space 52. on a middle portion 51a of the rotary pin 51, that is to say internally in said hollow space 52, there is rotatably mounted a main castor 53, while on one end portion 51b of the rotary pin 51 on the outwardly facing side 48a of the piston rod 48 there is rotatably mounted an auxiliary castor 55. The main castor 53 comprises an inner hub portion 53a having a roller bearing 53b and an outer rim portion 53c. The rim portion 53c is provided with a double curved, that is to say ball sector-shaped roller surface 53c" . The auxiliary castor 55 has a construction corresponding to the main castor 53 and comprises an inner hub portion 55a, a middle roller bearing 55b and an outer rim portion 55c with ball sector-shaped roller surface 55c" . The main castor 53 is adapted to be rolled off along a roller surface 54 concavely cuirved in cross-section, which forms a part of a so-called "sine" - curve 54" as shown in Fig. 6 - 8. By employing a ball sector-shaped roller surface 53c", which rolls along an eguivalently curved guide surface 54 of the cam guide device 12a and 12b, an effective support abutment can be ensured between the castor 53 and the guide surface 54 under varying working conditions, and possibly with a somewhat obliquely disposed castor and/or obliquely disposed piston rod 48 (49) , such as this being able to be permitted in the pivotable mounting of the piston rod 48 in the piston 44, as shown in Fig. 5h. The "sine" - curve 54" is designed in the cam guide device 12a and 12b of the drive shaft on a side facing equivalently axially outwards from the intermediate cylinder"s 21. The auxiliary castor 55 is adapted to be rolled off against and along an equivalent, other "sine" -curve (not shown further) concavely curved in cross-section along a roller surface 56a in a roller path, which is designed in the cam guide device 12a (and 12b) radially just within the roller surface 54. In the embodiment illustrated in Fig. 5a the "sine" -curve 54a" is placed radially outermost, while the "sine" curve 56a" is placed in the cam guide device 12a a distance radially within the "sine" - curve 54a". Alternatively the "sine" curve 54a" can be arranged radially within the "sine" - curve 56a" (in a manner not shown further). In each of the cam guide devices 12a and 12b there are designed a corresponding pair of "sine" - curves 54a", 56a" in a manner not shown further and each "sine" - curve can be provided with one or more "sine" - planes as xequirea. In Fig. 1 schematic reference is made to a cam guide device 12a and 12b, while the details in the associated "sine" - cuirves and "sine" planes are shown further in Fig. 9-14. The "sine" - concept Generally the "sine" - concept can be applied with an odd numbered number (1,3,5 etc.) of cylinders, while an even numbered (2,4,6 etc.) number of "sine" - planes is employed and vice - versa. In a case where there is employed in each of the cam guide devices 12a and 12b a single "sine" - plane (having a "sine" - top and a "sine" - bottom), that is to say the "sine" - plane covers an angular arc of 360°, it is however immaterial whether an odd numbered or even numbered number of cylinders is employed. Correspondingly with a number of two (or more) "sine" - planes there can for instance be employed a larger or smaller number of cylinders as required. The said case with a single "sine" - plane can be especially of interest for use in engines running rapidly which are driven at speeds over 2000 rpm. According to the "sine" - concept the individual engine can be " internally " geared with respect to speed, all according to which number of "sine" - tops and "sine" - bottoms is to be employed at each 3 60° revolution of the drive shaft. In other words according to the "sine"-concept both engines can be built precisely in the revolutions per minute region which is relevant for the individual application. Generally the series arranged cylinders of the engine, with associated pistons, of the illustrated embodiment are arranged in specific angular positions around the axis of the drive shaft, for instance with mutually equal intermediate spaces along the "sine" -plane or along the series of "sine" - planes ( the "sine"-curve). For example for a two cycle or four cycle engine numbering three cylinders (see Fig. 6) , there can be employed for each 360° revolution two "sine" - tops and two "sine" - bottoms and four oblique surfaces lying between, that is to say two "sine" - planes are arranged after each other in each cam guide device 12a,12b. Consequently in a four cycle motor four cycles can be obtained for each of the two pistons of the three cylinders with each revolution of the drive shaft/cam guide devices and four cycles for each of the two pistons of the three cylinders in a two cycle engine. Correspondingly for a two cycle engine numbering five cylinders, as is shown in Fig. 9 and 10, there can be employed, for each 3 60° revolution, a "sine" - cuirve with two "sine" - tops and two "sine" - bottoms and four oblique surfaces lying between, that is to say two "sine" - planes arranged after each other in each cam guide device 12a,12b, so that in a two cycle engine four cycles are obtained for each of the two pistons of the five cylinders with each revolution. The support rollers of the pistons are placed in the illustrated embodiment with equivalently equal angular intermediate spaces, that is to say in equivalent rotary angular positions along the "sine" - curve, so that they are subjected one after the other to equivalent piston movements in equivalent positions along the respective "sine" - planes. The engine power is consequently transferred from the different pistons 44,45 one after the other via the support rollers 53 in the axial direction for the drive shaft 11 via respective "sine" - curves each with their "sine" - plane, and the drive shaft 11 is thereby subjected to a compulsory rotation about its axis. This occurs by piston rods of the engine being moved parallel to the longitudinal axis of the drive shaft and support rollers of the piston rods being forcibly rolled off along the "sine" - planes. The engine power is thereby transferred in an axial direction from support rollers of the piston rods to the "sine" - planes, which are forcibly rotated together with the drive shaft 11 about its axis. In other words the transfer of motive power is obtained from an oscillating piston movement to a rotational movement of the drive shaft, the motive power being transferred directly from respective support rollers of the piston rods to "sine" - planes of the drive shaft. In Fig. 6a there is schematically illustrated a support roller 53 on an obliquely extending portion of a "sine" - curve 8a. Axial driving forces are shown from an associated piston 44 having piston rod 4 8 in the form of an arrow Fa and eguivalently in a radial plane decomposed rotational forces transferred to the "sine" - plane 8a shown by an arrow Fr. The rotational forces can be deduced from formula 2: Fr = Fa. tan (p. According to the invention one achieves inter alia , by means of a particular design of the "sine" - plane according to the invention, the expansion stroke of the pistons 44,45 - reckoned angularly relative to the rotational arc of the drive shaft - becoming larger than the compression stroke of the pistons 44,45. In spite of the different speeds of movement of the pistons in opposite directions of movement, a relatively more uniform transfer of motive force to the drive shaft 11 can hereby be ensured and in addition a "more uniform", that is to say more vibration-free running of the engine. In Fig. 6-8 there is schematically shown the mode of operation pf a three cylinder engine 10, in which only the one piston 44 is shown of the two cooperating pistons 44,45, illustrated in a planar spread condition along an associated "sine" - curve 54", which consists of two mutually succeeding "sine" - planes, plus the associated main castor 53 of the associated one piston rod 48. In each of the Figures 6-8 there is schematically shown the associated one piston 44 in each of three cylinders 21 of the engine, an equivalent arrangement being employed for the piston 45 at the opposite end of the cylinders. For the sake of clarity the cylinder 21 and the opposite piston 45 have been omitted from Fig. 6-8, only the piston 44, its piston rod 48 and its main castor 53 being shown. Axial movements of the piston 44 are illustrated by an arrow 57, which marks the compression stroke of the piston 44, and an arrow 58, which marks the expansion stroke of the piston 44. The "sine" - curve 54" is shown with a lower roll path 54, which has a double "sine" - plane-shaped contour and which generally guides the movement of the main castor 53 in an axial direction, in that it more or less constantly effects a downwardly directed force from the piston 44 via the main castor 53 towards the roll path 54 in the expansion stroke and an upwardly directed force from the roll path 54 via the main castor 53 towards the piston 44 in the compression stroke. The auxiliary castor 55 (not shown further in Fig. 6-8) is received with a sure fit relative to an upper roll path 54b, as is shown in Fig. 5a. For illustrative reasons the said roll path 56b is shown vertically above the main castor 53 in Fig. 6 - 8, so as to indicate the maximum movement of the main castor in an axial direction relative to the roll path 54. In practice it will be the auxiliary castor 55 which controls the possibility for movement of the main castor 53 axially relative to its roll path 54, as is shown in Fig. 5a. The auxiliary castor 55 is normally not active, but will control movement of the piston 44 in an axial direction in the instances the main castor 53 has a tendency to raise itself from the cam-forming roll path 54. During operation lifting of the main castor 53 in an unintentional manner relative to the roll path 54 can hereby be avoided. The roll path for the auxiliary castor 55 is, as shown in Fig. 5, normally arranged in the fixed fit spacing from the roll path of the main sector 53. In Fig. 6-8 the sine curve 54" is shown with a first relatively steep and relatively rectilinear running curve portion 60 and a subsequent, more or less arcuate, top-forming transition portion/dead portion 61 and a second relatively more gently extending, relatively rectilinearly running cuirve portion 62 and a subsequent arcuate transition portion/dead portion 63, These curve contours are however not representative in detail of the curve contours which are employed according to the invention, examples of the correct curve contours being shown in more detail in Fig. 12 and 13. The "sine" - curve 54" and the "sine" - plane 54 are shown in Fig. 6-8 with two tops 61 and two bottoms 63 and two pairs of curve portions 60,62. In Fig. 6-8 there are illustrated three pistons 44 and their respective main castor 53 shown in equivalent positions along an associated "sine" - curve in mutually different, succeed¬ing positions. It is evident from the drawing that the relatively short first curve portions 60 entail that at all times only one main castor 53 will be found on the one short curve portion and two or roughly two main castors 53 on the two longer curve portions 62. In other words with the illustrated curve contour different forms of curve portions can be employed for the compression stroke relative to the form of the curve portions for the expansion stroke. Inter alia one can hereby ensure that the two main castors 53 at all times overlap the expansion stroke, while the third main castor 53 forms a part of the compression stroke. In practice movement of the piston 44 is achieved with relatively greater speeds of movement in the axial direction in the compression stroke than in the expansion stroke. In themselves these different speeds of movement do not have a negative influence on the rotational movement of the drive shaft 11. On the contrary it means one is able to observe that more uniform and less vibration-inducing movements in the engine can be obtained, with such an unsymmetrical design of the curve portions 60,62 relative to each other. Further there is obtained an increase of the time which is relatively placed for disposition in the expansion stroke relative to the time which is reserved for the compression stroke. In a practical construction according to Fig. 6-8 there is chosen in a 180° working sequence an arc length for the expansion stroke of about 105° and an equivalent arc length for the compression stroke of about 75°. But actual arc lengths can for instance lie between 110° and 95° when the expansion stroke is concerned and equivalently between 70° and 85° when the compression stroke is concerned. On using for instance a set of three cylinders 21 associated with three pairs of pistons 44,45, as is described above, two tops 61 and two bottoms 63 are employed for each 3 60° revolution of the drive shaft 11, that is to say two expansion strokes per piston pair 44,45 per revolution. On using for instance four pairs of pistons there can be correspondingly employed three tops and three bottoms, that is to say three expansion strokes per piston pair per revolution. In the embodiment according to Fig. 9-10 there is discussed a five cylinder engine with five pairs of pistons, associated with two tops and two bottoms, that is to say with two expansion strokes per piston pair per revolution. Typical cam guide arrangement according to the invention In what follows there will be described with reference to Fig. 9 and 10 in more detail a preferred embodiment of the "sine" - concept according to the invention in connection with a five cylinder, two cycle-combustion engine with two associated, mutually differing cam guide curves 8a and 8b, as shown in Fig. 9 and 10 and in Fig. 12 and 13. In Fig. 14 there is schematically shown a midmost, theoretical cam guide curve 8c, which shows the volume change of the working chamber K from a minimum, as shown in the combustion chamber Kl in the dead zones 4a and 4b, to a maximum, as shown in the maximum working chamber K in the dead points Oa and Ob (see Fig. 9-10 and 12 - 14). According to the invention the curve 8b, as is illustrated in Fig. 12 - 14, is shown at the dead point Ob phase-displaced an angle of rotation of 14° in front of the dead point Oa of the curve 8a. The direction of rotation of the curves 8a and 8b, that is to say the direction of rotation of the drive shaft 11, is illustrated by the arrow E. In Fig. 9 and 10 there are schematically illustrated five cylinders 21-1, 21-2, 21-3, 21-4 and 21-5 and belonging to two associated curves 8a and two curves 8b, shown spread in a schematically illustrating manner in one and the same plane. The five cylinders 21-1, 21-2, 21-3, 21-4 and 21-5 are shown in respective angular positions with a mutual angular space of 72°, that is to say in positions which are uniformly distributed around the axis of the rotary shaft 11. In Fig. 12 there is shown a first curve 8a, which covers an arc length of 180° from a position 0°/360° to a position 180°. A corresponding curve 8a (see Fig. 9) passes over a corresponding arc length of 180° from position 180° to position 3 60°. In other words two succeeding curves 8a for each 360° revolution of the drive shaft. The curve 8a shows in position 0°/360° a first dead point Oa. From position 0° to a position 38.4° there is shown a first transition portion la, which corresponds to a first part of a compression stroke and from position 38.4° to position 59.2°an obliquely (upwardly) extending rectilinear portion 2a, which corresponds to a main part of the compression stroke and from position 59.2° to a position 75° a second transition portion 3a, which corresponds to a finishing part of the compression stroke. Thereafter from the position 75° to a position 85° there is shown in connection with a second dead point a rectilinear dead portion 4a, which is shown passing over an arc length of 10°. From the position 80° to a position 95.8° there is shown a transition portion 5a, from the position 95.8° to a position 160° an oblique downwardly extending, rectilinear portion 6a and from the position 160° to a position 180° a transition portion 7a. The three portions 5a,6a,7a together constitute an expansion portion. In position 180° is show anew the dead point Oa and thereafter the cam guide curve continues via a second corresponding cuirve 8a, from the position 180° to the position 3 60°, that is to say with two curves 8a which together extend over an arc length of 3 60°. In Fig. 13 there is shown an equivalent (mirror image) curve contour for the remaining curve 8b, shown with a dead point Ob and succeeding curve portion lb-7b. There is shown the dead point Ob in a position 346°, - the curve portion lb between the positions 346° and 60°, 75^ - the curve portion 2b between the positions 3° and - the curve portion 3b between the positions 60° and - the curve portion 4b between the positions 75° and 80" - the curve portion 5b between the positions 8 0° and 101.5°, - the curve portion 6b between the positions 101.5° and 146° and - the curve portion 7b between the positions 14 6° and 166°, that is to say with the dead point Ob shown anew in the position 166°. The cam guide continues with a corresponding curve 8b between the positions 166° and 346° (see Fig. 10) . The first curve 8a (Fig. 12) controls opening (position 160°/340°) and closing (position 205°/25°) of exhaust ports 25. The second curve 8b (Fig. 13) control opening (position 146°/326°) and closing (position 185°/5°) of scavenging ports 24. In Fig. 14 there is shown a phase-displacement of 14° between the dead points Oa and Ob, in the illustrated, schematic comparison of the curves 8a and 8b. Curve 8b, as shown by broken lines in Fig. 14, is for comparative reasons shown in mirror image form relative to the curve 8a, which for its part is shown in full lines in Fig. 14. By chain lines there is shown the midmost, theoretical curve 8c, which illustrates a curve contour approximately like or more like a mathematical "sine cuirve" - contour. In Fig. 9 and 10 there is shown the "sine" - plane 8b in a position 14° in front of the position for the "sine" -plane 8a. The five said cylinders 21-1, 21-2, 21-3, 21-4 and 21-5 are shown in successive positions relative to the associated "sine" plane and individually in successive working positions, as shown in the following diagram 1 and diagram 2. Diagram 1 with reference to Fig. 9 and Fig. 12 - 13 Cylinde ir Angle Working Exhaust Scavenging Cur-ve No. Position Position Ports Ports Zone 8a/8b 21-1 3°/183° compression closed open* la/lb 21-2 75°/255° compression closed closed 4a/4b 21-3 47°/327° expansion closed closed 6a/7b 21-4 219°/39° compression closed closed 2a/2b 21-5 291°/101° expansion closed closed 5b/6a * The scavenging ports 24 open in position 160°/340° and close in position 25°/205°, that is to say the scavenging ports 24 are held open over an arc length of 45°. The exhaust ports 25 are held on the other hand open over an arc length of 3 9°, that is to say over an arc length which is phase-displaced 14° relative to the arc length in which the scavenging ports are open (see Fig. 14) . The scavenging ports 24 can consequently be open over an arc length of 20° (see the curve portions la - 3a in Fig. 12 and the single hatched section A" in Fig. 14) after the exhaust ports 25 are closed. This means that the compression chamber over the last-mentioned arc length of 20° can inter alia be supplied an excess of scavenging air, that is to say is overloaded with compressed air. Diagram 2 with reference to Fig. 10 and Fig. 12 - 13. Cylinder Angle Working Exhaust Scavenging Curve No. Position Position Ports Ports Zone 8a/8b 21-1 21°/201° compression closed closed la/2b 21-2 93°/273° expansion closed closed 5a/5b 21-3 165°/345° expansion open** open* 7a/7b 21-4 237°/57° compression closed closed 2a/2b 21-5 309°/129° expansion closed closed 6a/6b ** The exhaust ports open in position 146°/326° and close in position 185°/5°, that is to say the exhaust ports 25 are open over an arc length of 3 9°. From Fig. 14 it will be evident from the marked off, individual hatched sections B" that the exhaust ports 25 can be held open over an arc length of 14° before the scavenging ports 24 open. The said sections A" and B" show the axial dimensions of the exhaust ports 25 and the axial dimensions of the scavenging ports 24 in a respective outer portion of the working chamber K. The ports 24 and 25 can thereby be designed of equal height in each end of the working chamber K. The said height is shown in Fig. 12 -14 by X2. In an angle zone of 5° (from position 75° to position 80° - see especially Fig. 13) of the "sine" - plane 8b and in an angle zone of 10° (from position 75° to position 85° -see especially Fig. 12) of curve 8a, the respective associated piston 44 and 45 is held pushed in to the maximum with a minimum spacing X of for instance 15 mm between the piston head 44a and the middle line of the working chamber. With reference to Fig. 12 it must further be observed that over an arc length of 36.6°, from position 59.2° to position 95.8°, the spacing between the piston heads is chaiiged relatively little. The spacing from the piston head 44a to the middle line 44" is changed from a minimum X = 15 ram (in the dead portion 75° - 80°) to a 20 mm spacing (position 93° Fig. 13) . Correspondingly the spacing from the piston head to the middle line 44" is changed from a minimum X = 15 mm in the dead portion 75° - 80° to a 25 mm spacing in position 57° Fig. 13. Over said arc length of 3 6.6°the volume in the combustion chamber Kl is kept approximately constant between the pistons 44,45. Combined effects of two phase-displaced "sine" - planes From Fig. 14 the contours of the respective two curves 8a,8b, which are shown schematically in mirror image relative to each other will be evident. Cu2rve 8a is shown real with a full line, while curve 8b is shown with a broken line, in mirror image about a middle axis between the pistons 44,45. The curve 8c shows a theoretical midmost curve between the curves 8a,8b. It will be evident that the midmost curve 8c has a contour which lies more closely up to a sine curve contour than the contours of the cuirves 8a, 8b individually. Consequently, even if one gets a relatively unsymmetrical contour in the curves 8a,8b mutually, a relatively symmetrical contour of the midmost curve 8c can be achieved. Fuel is injected; At the close of the compression phase in curve zone 3a and 3b the fuel is injected in a jet with a flow into the rotating scavenging air current and is mixed/atomised effectively in the rotating scavenging air current. ignition starter: Immediately after the injection of fuel that is to say at the close of the compression phase electronically controlled ignition is initiated in curve zone 3a and 3b. Provision being made for effective rotation of the gas mixture of scavenging air and fuel in a fuel cloud past the ignition arrangement. According to the present invention one can aim with advantage at an ignition delay of 7 - 10% relative to the conventional ignition angle. Combustion phase In the illustrated embodiment the combustion starts immediately after ignition and is accomplished mainly over a limited region in which the pistons roughly occupy a maximum pushed in position, that is to say at the close of the curve zone 3a,3b, that is to say in a region where the pistons are subjected to minimal axial movement. The combustion proceeds mainly or to a significant extent where the pistons 44,45 are held at rest in the inner dead portion 4a and 4b, that is to say over an arc length of 10° and 5° respectively. However the combustion continues as required to a greater or smaller degree in the following transition portion 5a,5b and in the main expansion portion 6a,6b, depending upon the speed of rotation of the rotary shaft. As a consequence of the rotating fuel cloud in the combustion chamber Kl in the dead portion 4a,4b and in that one can keep the flame front relatively short in the disc-shaped combustion chamber Kl, there can be ensured in all instances fuel ignition for a main bulk of the fuel cloud in the combustion chamber Kl, that is to say within said dead portion 4a,4b. In practice the combustion chamber can be allowed to be expanded to the portion 5a,5b just outside the dead portion 4a,4b with largely corre¬sponding advantages in a defined volume of the working chamber K. Speed of combustion The speed of combustion is as known of an order of magnitude of 20 - 25 meters per second. By the application of a double set of fuel nozzles and a corresponding double set of ignition arrangements distributed over each quarter of the peripheral angle of the working chamber (see Fig. 4b) the combustion area can be effectively covered over the whole of the disc-shaped combustion chamber Kl. In practice especially favourable combustion can thereby be achieved with relatively short flame lengths. Optimal combustion temperature: As a result of the concentrated ignition/combustion zone 3a,3b which is defined in the chamber K just in front of the combustion chamber Kl and the region 5a,5b immediately after the combustion chamber Kl, that is to say in a coherent region 3a - 5a and 3b - 5b, where the pistons 44,45 are at rest or largely at rest, it is possible to increase the combustion temperature from usually about 1800°C to 3 000°C. It is possible thereby to achieve an optimal (almost 100%) combustion of the fuel cloud even before the pistons 44,45 have commenced fully the expansion stroke, that is to say at the end of the curve portions 5a,5b. Ceramic ring Provision is made for a ceramic ring, that is to say a ceramic coating applied in an annular zone of the working chamber K corresponding to a combustion region (3a - 5a,3b,5b), so that high temperatures can be employed especially in the combustion chamber Kl, but also in the following portion 5a,5b of the combustion region. The ceramic ring which is shown with a dimension as indicated by a broken line 70 in Fig. 12 - 14, comprises the whole combustion chamber Kl and is in addition extended further outwards in the combustion chamber over a distance 13. Introductory Expansion Stroke After at least considerable portions of the fuel are consumed in the afore-mentioned combustion region (3a -5a, 3b,5b) and one has just started the expansion stroke there are generally optimal motive forces. More specifi¬cally this means that by way of the cam guide along the curves 8a and 8b there is obtained an optimal driving moment immediately the expansion stroke commences in the transition region 5a,5b and increases towards a maximum in the transition region 5a,5b. The driving moment is maintained largely constant in the continuation-of the expansion stroke (in the region 6a,6b) and at least in the beginning of this region, as a consequence of possible after burn of fuel in this region in spite of the volumetric expansion which occurs gradually in the chamber K as the expansion stroke proceeds forward through this. Expansion Phase According to the illustrated embodiment the compression phase takes place relative to the curves 8a,Bb under angles of inclination of between about 25° and about 36° in the respective two curves Ba and Bb, that is to say with a mean angle (see Fig. 14) of about 30°. If desired the angles of inclination (and the mean angle) can for instance be increased to about 45° or more as required. The expansion phase takes place correspondingly in the illustrated embodiment at between about 22° and 27° in the two curves 8a and 8b, that is to say while at a mean angle (see Fig. 14) of about 24°. As a result of the relatively steep (mean) curve contour of 3 0° in the compression phase and the relatively gentler contour 24° in the expansion phase, there is achieved a particularly favourable increase of the durability in time of the expansion stroke relative to the durability of the compression stroke. According to the invention one can by means of said unsymmetrical relationship between the speed of movement in the compression stroke and the speed of movement in the expansion stroke, displace the start of the combustion process in the compression phase closer up to the inner dead point and thereby time-displace a larger part of the combustion process to the beginning of the expansion phase, without this having negative consequences for the combustion. Consequently there can be achieved a better control and a more effective utilisation of the motive force of the fuel combustion in the expansion phase than hitherto. Inter alia there can be displaced an otherwise possibly occurring, uncontrolled combustion from the compression phase over the dead point to the expansion phase and thereby convert such " pressure points", which involve uncontrolled combustion in the compression phase, to useful work in the expansion phase. By extending the expansion phase at the expense of the compression phase a relatively higher piston movement is obtained in the compression phase than in the expansion phase. This has an influence on each set of pistons of the combustion engine in every single working cycle. Rotation effect in the working chamber There is established rotation of the gases in the working chamber by ejecting exhaust gases via obliquely disposed exhaust ports 25 (see Fig. 2) followed by the injection of scavenging air via the obliquely disposed scavenging air ports 24 (see Fig, 3). There is set up thereby a rotating, that is to say helical gas flow path (see arrow 3 8 in cylinder 21 -1 in Fig. 9) which is maintained over the whole working cycle. The rotational effect is reactivated in the course of the working cycle, that is to say during the injection, ignition and combustion phases. There is consequently supplied a new rotational effect to the gas flow 3 8 during transit in the working cycle by fuel injection via the nozzle 3 6 and subsequent fuel ignition via the ignition arrangement 39, the attendant combustion producing a direction fixed flame front with an associated pressure wave front roughly coinciding with the gas flow 38 already established. The rotational effect is consequently maintained during the whole compression stroke and is reactivated during transit by injecting fuel via an obliquely disposed nozzle jet 37, as shown in Fig. 4a, via a corresponding obliquely disposed nozzle mouth 36. Additional rotational effects are obtained in the combustion phase. A still additional increase of the rotational effect can be obtained according to the construction as shown in Fig. 4b by the application of an extra (second) "fuel nozzle 3 7a, which is disposed angularly displaced relative to the first fuel nozzle 37, and by the application of an extra ignition arrangement 3 9a, which is disposed angular¬ly displaced relative to the first ignition arrangement 39. When the exhaust ports 25 open again, on the termi¬nation of the working cycle, the exhaust gas is exhausted with a high speed of movement, that is to say with a high rotational speed, during exhaustion of exhaust gas via the said obliquely disposed exhaust ports. Further the rotational effect for the exhaust gases is maintained immediately the obliquely disposed scavenging ports 24 open, so that the residues of the exhaust gases are scavenged with a rotational effect outwardly from he working chamber K at the close of the expansion phase and the beginning of the compression phase. Thereafter the rotational effect is maintained, after closing of the exhaust ports, the scavenging ports being continued to be held open over a significant arc length. Regulation of the compression ratio of the engine during operation According to the invention it is possible to regulate the volume between pistons 44,45 of the cylinder 21 by regulating the mutual spacing between the pistons 44,45. It is hereby possible to directly regulate the compression ratio in the cylinder 21 as required, for instance during operation of the engine by means of a simple regulation technique adapted according to the "sine" - concept. It is especially interesting according to the invention to change the compression ratio in connection with starting up the engine, that is to say on cold start, relative to a most favourable compression ratio possible during usual operation. But it can also be of interest to change the compression ratio during operation for various other reasons. A constructional solution for such a regulation according to the invention is based on pressure oil -controlled regulating technique. Alternatively there can be employed for instance electron-controlled regulating technique, which is not shown further herein, for regulat¬ing the compression ratio. Alternatively there can be employed a corresponding regulating possibility also for the piston 45 by replacing the cam guide device 12a with a cam guide device corre¬spondingly as shown for the cam guide device 12b. It is apparent according to the invention that it is possible to regulate the position of both pistons 44,45 in the associated cylinder via their respective cam guide arrangement with their respective separate possibility of regulation, in a mutually independent manner. It is also apparent that the regulation of the position of the pistons in the cylinder can be effected synchronously for the two pistons 44,45 or individually as required. In Fig. 15 and 16 there is shown schematically an alternative solution of certain details in a cam guide device, as it is referred to herein by the reference numeral 112a, and of an associated piston rod, as shown by the reference numeral 148 as well as a pair of pressure rollers, as shown by the reference numerals 153 and 155. The cam guide device 112a: In the construction according to Fig. 1 the cam guide device 12a is shown having a relatively space-demanding design with associated casters 53 and 55 arranged at the side of each other in the radial direction of the cam guide device 12a, that is to say with the one caster 53 arranged radially outside the remaining caster 55 and with the associated "sine" - grooves 54,55c illustrated correspondingly radially separated on each of their radial projections In the alternative construction according to Fig. 15 and 16 the cam guide device 112a is shown with associated pressure spheres 153, 155 arranged in succession in the axial direction of the cam guide device 112a, that is to say with a sphere on each respective side of an individual, common projection, illustrated in the form of an intermediate annular flange 112. The annular flange 112 is shown with an upper "sine" - curve forming "sine" - groove 154 for guiding an upper pressure sphere 153, which forms the main support sphere of the piston rod 14 8, and a lower "sine" -curve forming "sine" - groove 155a for guiding a lower pressure sphere 155, which forms the auxiliary support sphere of the piston rod 148. The grooves 154 and 155a have, as shown in Fig. 15, a laterally concavely rounded form corresponding to the spherical contour of the spheres 153,155. The annular flange 112 is shown having a relatively low thickness, but the low thickness can be compensated for as to strength in that the annular flange 112 has in the peripheral direction a self-reinforcing "sine" - curve contour, such as indicated by the obliquely extending section of the annular flange illustrated in Fig. 16. In Fig. 15 the annular flange 112 is shown segmentally in section, while in Fig. 16 there is shown in cross-section a peripherally locally defined segment of the annular flange 112, seen from the inner side of the annular flange 112. There can be employed a largely corresponding design of the afore-mentioned details in both cam guide devices, that is to say also in the cam guide device not shown further corresponding to the lower cam guide device according to Fig. 1. The piston rod 148: According to Fig. 1 a pipe-shaped, relatively voluminous piston rod 48 is shown, while in the alternative embodiment according to Fig. 15 and 16 there is illustrated a slimmer, compact, rod-shaped piston rod 14 8 having a C-shaped head portion 14 8a with two mutually opposite sphere holders 148b,148c for a respective pressure sphere 153,155. The piston rod 148 can in a manner not shown further be provided with external screw threads which cooperate with internal screw threads in the head portion, so that the piston rod and thereby the associated sphere holder 148b can be adjusted into desired axial positions relative to the head portion 148a. This can inter alia facilitate the mounting of the sphere holder 148b and its associated sphere 153 relative to the annular flange 112. In Fig. 16 the annular flange 112 is shown with a minimum thickness at obliquely extending portions of the annular flange, while the annular flange 112 can have in a manner not shown further a greater thickness at the peaks and valleys of the "sine" -curve, so that a uniform or largely uniform distance can be ensured between the spheres 153,154 along the whole periphery of the annular flange. By the reference numeral 100 there is referred to herein a lubricating oil intake, which internally in the C-shaped head portion 148a branches off into a first duct 101 to a lubricating oil outlet 102 in the upper sphere holder 148b and into a second duct 103 to a lubricating oil outlet 104 in the lower sphere holder 148c. The pressure spheres 153,155: Instead of the casters 53,55 shown according to Fig. 1, which are mounted in ball bearings, pressure spheres 153,155 are shown according to Fig. 15 and 16. The pressure spheres 153,155 are mainly adapted to be rolled relatively rectilinearly along the associated "sine" -grooves 154,155a, but can in addition be permitted to be rolled sideways to a certain degree in the respective groove as required. The spheres 153 and 155 are designed identically, so that the sphere holders 148a,148b and their associated sphere beds can also be designed mutually identically and so that the "sine" - curves 154,155a can also be designed mutually identically. The pressure spheres 153,155 are shown hollow and shell-shaped with a relatively low wall thickness. There are obtained hereby pressure spheres of low weight and small volume, and in addition there is achieved a certain elasticity in the sphere for locally relieving extreme pressure forces which arise in the sphere per se. In Fig. 17 and 18 a pair of guide rods 105,106 are shown which pass through internal guide grooves 107,108 along opposite sides of the head portion 148a of the piston rod 148. Patent Claims 1. Arrangement of a two cycle combustion engine (10,100) having internal combustion, comprising a number of engine cylinders (21; 21-1 - 21-5), which are arranged in an annular series around a common middle drive shaft (11) and which have cylinder axes running parallel to the drive shaft, each cylinder including a pair of pistons (44,45) movable towards and away from each other and a common, intermediate working chamber (K) for each pair of pistons, while each piston (44,45) is provided with its axially movable piston rod (48,49), the free outer end of which forms via a support roller (53,55) a support against its curve-shaped, that is to say "sine" - curve shaped, cam guide device (12a,12b), which is arranged at each of opposite ends of the cylinder (21; 21-1 - 21-5) and which controls movements of the piston relative to the associated cylinder, characterised in that the two pistons (44,45) in each cylinder (21; 21-1 -21-5) have mutually differing piston phases, which are controlled by mutually differing cam guide devices (12a,12b) , the cam guide devices (12a,12b) being designed with equivalent mutually differing "sine" - planes ( "sine" -curves 8a,8b). 2. Arrangement in accordance with claim 1, characterised in that the respective cam guide devices (12a,12b) of the two pistons (44,45), at least in certain portions (la - 3a, 5a - 7a; lb - 3b, 5b - 7b) of the "sine" - plane ("sine" -curves 8a,8b) are phase-displaced relative to each other. 3. Arrangement in accordance with claim 2, characterised in that the phase displacement is defined for certain portions (la-3a, 5a-7a; lb-3b, 5b-7b) by the "sine" - pianes ("sine" curves 8a,8D), so that remaining portions (4a,4b) of the "sine" - planes are in mutual phase. 4. Arrangement in accordance with claim 3, characterised in that at least one piston (44) of the cylinder, and preferably both pistons (44,45) of the cylinder, is/are held individually axially stationary or largely stationary, in a portion (Kl) of the working chamber (K) at the dead point between the compression stroke and the expansion stroke, controlled by an equivalent rectilinear or largely rectilinear portion (4a,4b) of the associated "sine" - plane. 5. Arrangement in accordance with claim 4, characterised in that there is arranged in the portion (Kl) of the working chamber (K), where the piston/pistons (44,45) are stationary or largely stationary, a combustion chamber (Kl) for combustion of at least parts of the fuel and preferably for combustion of the major portion of the fuel just before the subsequent expansion phase. 6. Arrangement in accordance with claim 5, characterised in that the combustion chamber (Kl) is arranged over a relatively large arc length (5° - 10°) of the longitudinal dimension of the "sine" - planes (the "sine" - curves 8a,8b) and of the rotational arc of the drive shaft (11). Arrangement of a two cycle combustion engine substantially lerein described with reference to the accompanying drawings.

Documents:

2376-mas-1998 abstract-duplicate.pdf

2376-mas-1998 abstract.pdf

2376-mas-1998 assignment.pdf

2376-mas-1998 claims-duplicate.pdf

2376-mas-1998 claims.pdf

2376-mas-1998 correspondence-others.pdf

2376-mas-1998 correspondence-po.pdf

2376-mas-1998 description (complete)-duplicate.pdf

2376-mas-1998 description (complete).pdf

2376-mas-1998 drawings-duplicate.pdf

2376-mas-1998 drawings.pdf

2376-mas-1998 form-1.pdf

2376-mas-1998 form-19.pdf

2376-mas-1998 form-26.pdf

2376-mas-1998 form-4.pdf

2376-mas-1998 form-6.pdf

2376-mas-1998 others.pdf

2376-mas-1998 petition.pdf