PISTON ENGINE

Abstract: By a piston machine with at least one axially movable piston in a cylinder, where at the top of the cylinder there is at least one intake valve and at least one exhaust valve, there is designed a further injection port (1'', 5, 5'') in cylinder walls between the lower and upper point of reversal of the piston. The air is suitably supplied from an air chamber between the cylinder wall and a lower narrowed part of the piston. For adjustment to the engine load, this air chamber may be connected with an extra air chamber suitably having an adjustable volume. Likewise, the engine may be provided with a rotary valve for supplying the air to the cylinder. By the construction a faster exhausting of the combustion gasses and a better degree of filling of the cylinders may be attained.

Description: PISTON ENGINE BACKGROUND OF THE INVENTION The development of four-stroke automotive engines has been markedly directed to- ward solutions that could improve their "breathing". This has thus lead to that even automobile engines for ordinary use to a large extent have been provided with 4 valves per cylinder and recently also more or less sophisticated systems for controlling the use of them, e.g. as made in the VTEC-E engines from HONDA. Furthermore, the desire for higher power yield has resulted in a wide use of engines provided with turbosupercharging. Both trends in development have led to the use of more and more complicated and costly applications of components, resulting in increased maintenance and repair costs. As a result of my development work, I have, however, indicated solutions which in a very simple manner are able to not only improve the usual air filling of four-stroke engines but also makes supercharging possible on a regular scale. Fundamentally, four-stroke engines can be supplied extra air supply by supplementing the amount of air sucked in through the traditional valve system with air supplied through ports situated and made like the scavenging air ports in a two-stroke engine. By the design of the ports, the indicated method of supply makes possible that the swirling in the combustion chamber can be influenced in a suitable way while at the same time the cooling of the piston tops, cylinder walls, and valves can be increased. The air supply may be performed at the termination of both termination of each intake stroke and at the initiation of each exhaust stroke. The air supply can furthermore be brought to take place only at the termination of each intake stroke. In the latter case, by using an e.g. rotary valve rotating with an rpm being 50% of the engine φm, it is ensured that the air supply is only performed at the termination of the intake stroke. Irrespectively which of the two solutions is selected, the air supply must be performed by a timing relative to the ordinary valve system of the engine. The indicated solutions may be realised in four-stroke engines, irrespectively whether the piston drive forces are drawn by the use of traditional crank and connecting rod mechanisms, by the use of a new "double connecting rod mechanism" developed by me, or by mechanisms allowing use of cylindrical piston rods reciprocated directly in the cylinder axis, as e.g. traditional crosshead engines, "crank loop" engines by FICHT GmbH & Co. KG, "twisting piston engines" by Teisen, and engines with the "I-yoke mechanism" developed by me. Fig. 1 shows schematically how a four-stroke engine with a traditional crank- connecting rod mechanism 17' provided with the stepped piston 1 has been provided intake ports 1 ' which by supply ducts are connected with the annular chamber 8 formed under the relatively short piston top part because of the stepping of the piston. The chamber 8 forms an air pump chamber which through the check valve 2' and a supply duct by the movement of the piston from BDC to TDC can suck in fresh air shown by the supply arrow designated A. As the air pump chamber because of the overall height of the engine has to be given a small height in relation to the reversal of the piston in BDC, the compressed air under the piston top part will get an unsuitable high pressure if the air pump chamber is not associated with a receiver 11 '. The receiver may suitably be provided with a regulating mechanism capable of regulating the volume of the receiver for receiving air, whereby it becomes capable of regulating the pressure of the air compressed in the air pump chamber. Receivers of this kind may e.g. be a cylinder with a piston which, placed on a piston rod that may be moved in and out of the cylinder by a mechanism, is capable of reducing or increasing the volume available for receiving the compressed air. Receivers that may be regulated in volume may interact with juxtaposed pump cham- bers, e.g. in in-line engines, are made as one cylinder with one through-going piston rod which, passed through partitioning walls with stuffing box arrangements, carries a plurality of piston discs, one in each of the chambers into which the partitioning walls divide the cylinder to contain. Each chamber in the cylinder is connected with a duct to their respective interacting pump chamber. The connecting duct is of course disposed at one end of their chambers which are kept clear of the piston irrespectively of the adjustment of the piston. At the other end of the chamber, via borings through the cylinder wall, it is ensured that fresh air can penetrate in and out so that air cannot be compressed which otherwise would inhibit the movement of the pistons by regulating in the direction toward that end of the receiver chamber. A receiver of the latter type has been illustrated in the sketch Fig. 4 which will be commented on later. Engines with plural cylinders may also have their air pump chambers connected with a receiver common to all chambers, e.g. of the type first mentioned with an adjustable volume, or to a receiver with a sufficiently large fixed volume. However, common to receivers with adjustable volume, with regulating mechanisms computer controlled with sensors registering the momentary m and load of the en- gines combined with the simultaneous speeding up of the engines, is that they make the engines more slow hauling and economic in operation, while at the same time the air-fuel ratio is better maintained to be the most suitable for clean combustion and therefore making less environmental impact by the release of exhaust gases. The four-stroke engine shown in Fig. 1 is of the kind receiving extra air supply both at the end of each intake stroke and in the beginning of each exhaust stroke. If such an engine is provided with a rotary valve like the rotary valve 3" shown and placed in the same position as in Fig. 8a and rotated with the same φm as the crank mechanism of the engine, it is possible, either by giving the rotary valve a fixed twist or by providing it with a twisting or turning mechanism, either mechanically with centrifugally influenced blocks or computer controlled, which depending on the momentary φm of the engine ensures that the supply of extra air is "delayed" and occurs at the most suitable time in relation to the closing of the intake valve and opening of the exhaust valve so that the supplied extra air amount is utilised optimally for charging or cooling, respectively. The sketch Fig. 2, like Fig. 1, is an engine with traditional crank and connecting rod mechanism provided with a stepped piston. For the components forming a part of it, the sketch is numbered as Fig. 1. If the rotary valve 3" is geared for rotating with an rpm which is 50% of the crank mechanism of the engine and it is given an opening time starting at the termination of the intake stroke, the engine can be provided with a regular aftercharge. The rotary valve may of course be given the same mechanisms for "twisting" or "turning". Since intake of air is performed at the passage of the check valve 2', this sucking in will chiefly occur only during the compression stroke as the air sucked in during this stroke cools the piston skirt and the cylinder wall etc. and hence is heated, which fur- ther takes place during the subsequent working and exhaust strokes and during the intake stroke where the air is finally compressed before it is injected through the injection port 1" at the end of this stroke. The sketch Fig. 3 illustrates a four-stroke engine with "double connecting rod mechanism" 50+50 described in Danish patent application no. 1278/96 with priority date 13 November 1996. As "double connecting rod mechanism" causes relief of the lateral pressure on the stepped piston 1 simultaneously with the occurrence exactly in the piston axis of an absoφtion and a transfer of the yielded drive forces and the occurring inertial forces to the piston pin 102, which results in that the stepped piston has been given a hollow, cylindrical piston rod fixed, possibly moulded, in the piston, the piston rod carrying a fitting at the end receiving the piston pin. Compared with the one illustrated in Fig. 2, the engine illustrated in Fig. 3 is further provided with the check valve 2" and an extra receiver 10' which may be with constant or adjustable volume and of course, besides that, with ducts for supply and discharge. By the supplement it is achieved that the amount of air sucked in during the compression stroke is forced to be transferred through the check valve 2" to the receiver 10' by the subsequent compression during the combustion stroke, because the pressure herein at the previous discharge of supplementary fresh air has been reduced to a lower pressure. At the subsequent exhaust stroke, depending on the relative momentary volumes of the receiver, a further amount of air can be sucked in and compressed during the intake stroke and therefore to a certain extent can supplement the amount of air already stored in the receiver 10' during the progress, and by the simultaneously in- creased pressure in the receiver ensure that the extra air charge for the combustion chamber is increased. In engines with rotary valves, these ensures that no short-circuiting takes place between combustion and pump chambers irrespectively of low piston height as well as they interact with check valves inserted in the supply for receivers intermediately storing fresh air, ensuring that no untimely discharge from these combustion or pump chambers occur. In engines with rotary valves the injection ports may be made high or placed higher over the piston top level at the reversal of the piston in BDC, because the injection ports are disposed closely to the external cylinder side of the rotary valve and there- fore, when they are closed by the rotary valve, only increase the combustion and pump chamber with such a small extra volume that their presence is inessential for the reduction of the effective length of stroke and because they are only opened and kept open at times where injection of extra air is desired. Because of the interaction of the injection ports with the rotary valves, engines with such may only be provided with the same number of ports as valves which commonly will result in the use of a single port. By engines without rotary valves, these may be designed with a simpler construction but in return the injection ports have to be made lower because they reduce the effective length of stroke in the combustion chamber and together with the volume of their supply ducts to an even higher degree reduce the extent of the compression that may be achieved in the pump chamber. The latter is not important since the drawbacks can be countered by reducing the volume in the used receivers, and the former can be countered by the lower overall height to a certain extent being countered by increasing the number of injection ports, which is readily possible in engines without rotary valves. As with two-stroke engines with scavenging ports, four- stroke engines with injection ducts have to be given piston rings which are secured against turning in their annular fastening so that they hereby engage the port apertures with their ends. The circumferential division of the cylinder wall by port apertures should be per- formed so that about 25 % of the cylinder wall remain circumferentially evenly distributed for supporting the piston rings. Irrespectively of the kind of receiver associated with the pump chamber for regulating the compression pressure, there may, if desired, be inserted a throttle valve in the engine intake to the pump chamber so that a further adjusting of the air amount sucked in and hereby also of the compression pressure may be performed. Fig. 4 is a sketch showing close to reality how a four-stroke engine with pump arrangement of its own, but without rotary valve, can be provided fresh air at the initiation of the exhaust stroke and extra fresh air at the termination or finishing of the intake stroke through low injection ports disposed immediately over the piston top when the piston reverses in BDC. The engine in Fig. 4 is directly comparable with the engine in enclosed Fig. 5 which without injection ports functions as a traditional four-stroke engine. In order to compare them mutually, both engines are drawn in the same scale and given the same piston diameter and length of stroke (quadratic engines). Their force transformation mechanisms are identical, namely the I-yoke mechanism described in my Danish patent application no. 1269/96 of 12 November 1996. The numbering of constituent components on the sketch in Fig. 4 is the same as explained in Fig. 5 in patent application no. 1269/96 when disregarding the numbers concerning components added to the sketch in order to explain their contributions for performing an air supply in addition to the one that may be achieved by intake through a valve arrangement usual to four-stroke engines. Compared with Fig. 5, the additions are the injection ports 5+5' and 5" with their associated supply ducts 6+6' and 6" connecting them with the very low space which is left of the pump chamber when the piston reverses in BDC, which space and supply ducts through a narrow, vertical connection 7 associating them with the active end of the annular chamber which, as it appears from the sectional view uppermost on the sketch, appears by inserting a preferably cylindrical spindle/tensile rod 9 in the centre axis of a cylindrical, tubular body extending past several combustion chambers, the rod 9 to be imparted a controlled axial movement by a regulating mechanism, e.g. a hydraulic cylinder, and hereby move the pistons 8, one in each regulating area, being fastened to the spindle/tensile rod which in the ends of the tubular body is passed through covers and inside the tube is passed through fastened partitioning walls 10 dividing the tube into the necessary number of regulating areas, one for each cylinder, which in the passive end is provided with borings 10 ensuring that atmospheric air may freely flow into and out from here by the movement of the pistons. Furthermore, it appears from Fig. 4 that for establishing a pump chamber under the pistons 1 there is formed a bottom cooled by the engine cooling water and wherein there is placed a bushing 13 forming a guide for the cylindrical piston rod 2 reciprocating exactly in the piston axis and which at the same time with possible inserted packings seals off down against the underlying crank disc chamber shown on the sketch. Insertion of the bottom piece with the sealing guide causes that a very little amount of oil can penetrate up and cause pollution by being supplied to the combustion chamber absorbed in the air compressed in the pump chamber. At the same time, the good sealing down against the crank disc chamber combined with the pump chamber prevents combustion residues in penetrating into the crank disc chamber and polluting the oil used there which thus may be used for more running hours without causing wear on the components working in the crank disc chamber. By its relatively large axial length, the sealing guide causes an even further secured guiding of the pistons at the reciprocation of these in the piston axis, so that the lateral pressure on the pistons already removed in practice is reduced and by selection of suitable materials for cylinder linings, pistons and piston rings makes a lubrication free movement of the parts abutting on the cylinder wall conceivable, and at least makes possible that lesser contaminating lubricating agents may be used in a small scale. As engines with injection ports and I-yoke mechanisms, like the four-stroke engine sketched in Fig. 6, advantageously can be constructed with two pistons which at their piston rods at each side of the I-yoke are fastened to this and thereby is brought to work in the same common piston rod axis, the engines may be provided with two guides in this and hereby ensure such a guiding of the pistons that they in practice reciprocate exactly in their piston axis, whereby only their piston rings are pressed against the cylinder wall. Four-stroke engines with injection ports with and without rotary valves can be made compact irrespectively of their embodiment. If e.g. the engine sketched in Fig. 8c is compared with the one shown in Fig. 5, it is seen that the engine in Fig. 4 only has an overall height which is increased with the axial height of the bottom cooled by the cooling water. By the comparison of the two sketched engines it is also seen that the engine in Fig. 4 has got its piston rod extended corresponding to the increase of the overall height, which because of the light piston rod construction only causes a small increase in the reciprocating masses in the piston rod axis. In order to estimate the size of the air amount supplied to an engine as outlined in Fig. 4 as supplement to the amount of air for both engines, aspirated through a traditional valve arrangement, the engines were evaluated to be drawn in the scale 1 :2 and rough calculations were performed. The calculations showed that the engine according to Fig. 4 as Otto engine is supplied a supplementary amount of air which, depending on the adjusting of the receiver, is from 3,86% to 18,07% greater than the amount supplied through the valve system, while in the engine, made as diesel engine, it may be provided a supplementary amount of air which is from about 6% to about 12% greater than the amount supplied through the valve system. The rough calculation performed designated "four-stroke engines according to 'COR¬ RECTED' Fig. 8c" is enclosed. The double number of working cycles compared with the four-stroke engine increases the yield and the torque - but implies a strongly increased thermal load, especially on the piston. This is countered in GV's two-stroke engine with ceramic coating of the piston top, injection of relatively cool charging air through aftercharge ports directed downward against the piston top, reduction of the lateral pressure on the piston by using the I- yoke force transmission mechanism, coating of piston rings and piston sides with amoφhous diamond which is scratch-proof, smooth and resistant up to 800°Celsius. Furthermore, heat is conducted away to a greater extent from the piston top to the pressure oil lubricated "crank disc chamber" by filling sodium into the light cylindrical piston rod while at the same time the rather long piston skirt at its external side during the working stroke of the piston is cooled by cool charging air freshly sucked in, while it during the compression stroke of the piston is cooled internally by cool scavenging air freshly sucked in. Difficulties with making catalysts that may tolerate the double number of exhausts which in addition are hotter than achieved by four-stroke engines - but the worst is the supply of residues of incompletely combusted lubricating oil as it occurs in engi- with crank case compression. Countered in GV's two-stroke engine by letting scavenging as well as charging air be sucked in and compressed in pump chambers separated from the pressure oil lubricated "crank disc chamber" and by reducing/removing the need for lubrication by re- lieving the piston of lateral pressure and instead substituting it with coating with amorphous diamond which without risk of deformation stresses may be applied at "room temperature". What really has checked the interest for developing two-stroke engines with port con- trol of scavenging as well as exhaust was the limits for exhaust pollution as in force from the year 2001. Ford terminated their tests with the port controlled Ford-Orbital two-stroke engine. Toyota continued their tests with a petrol two-stroke with scavenging ports and whole 4 top-disposed exhaust valves. Mercedes-Benz continued their experiments with a diesel two-stroke without ports, but with 2 intake and 2 exhaust valves placed at the top. Both engines troubled by the increased load of doubling the strokes compared with a four-stroke engine. Besides, just as complicated and costly to produce as four- stroke engines and further costly by having to be provided with air compressors for yield reasons. GN's two-stroke engine is basically provided with a simple and cheap port control being improved with respect to scavenging by an increased scavenging air volume and further improved by being performed with oilless scavenging air. The basic port control is amplified with just as simple and cheap arrangement of aftercharge air ports, the opening and closing of which being governed by an uncomplicated and cheap ro- tary valve with a simple duct design leading the access of the charge air previously compressed and accumulated in a receiver to the aftercharge ports. GN's two-stroke engine works without use of costly turbos or compressors, in addition, irrespectively of the cylinder number it is computer controlled capable of provid- ing itself with aftercharge air with a volume suitable for the momentary φm and load of the engine, which minimises the pump work. Besides, the pump work and the internal flow losses are minimised in that the engine has been provided very short and to the greatest extent straight intake and supply ducts while the internal friction losses are minimised as well by the moved components being coated with durable and latest developed "Super-Slick" materials. Most important: The reduction of the pollution problems for four-stroke engines will, as shown by CMCR, Australia, be made possible by the use of a force transformation mechanism which causes performing of a harmonic carrying through of piston motion in combination with a direct and adjustable fuel injection, which primarily has appeared to reduce the CO-number, besides that, CMCR has ascertained that a valve system enhancing the "swirling" between piston top and the cylinder head has appeared to reduce the NO x -number. As accepted by Dr. Ing. Spencer Sorenson, DTU (Technical University of Denmark), on the meeting held at DTU on 28 April 1999, this indicates that corresponding to this for the CO-number could be attained by the controlled aftercharge suggested by GV, performed in a two-stroke engine with harmonic piston motion and a graduated direct fuel injection as indicated used in GV's two-stroke engine, whereas the NO x -number, which Spencer Sorenson pointed out to be a weighty factor in pollution connection, could not be improved thereby. Regrettably, prior to the meeting at DTU I had overlooked that in the information material received from CMCR I had been informed about CMCR in their four-stroke Scotch Yoke engines had demonstrated possibilities for achieving improved NO x - numbers disclosed in "Newsletter of CMC Research Pty. Ltd.", Volume 2/98, July: Simulation confirms NO x advantage The expected advantage of lower NO x emissions achievable with the sinusoidal piston motion inherent with SYTech engines has been confirmed with the combustion simulation program developed at Melbourne University and CMCR. The existing program had been extended to include turbulence created by squish between piston and cylinder head. Further experimental work will be done to quantify the influence of the sinusoidal piston motion on NO x emissions. This message from CMCR (which I am in close contact with - their chief engineer Dr. Hans Rosenkranz visited me a couple of days in the middle of April this year) clarifies that also the NO x number can be expected to be reduced by designing the aftercharge ports in my two-stroke engine (also in four-stroke engines) with both downward di- rected and tangentially inserted, possibly mutually oppositely phased and thus achieving that an efficient "swirling" arises between the piston top and the cylinder head. If continued development work hand in hand with research could demonstrate this, my two-stroke engine will be the ultimate solution to the greatest disadvantages of this type of engine.

Claims: CLAIMS 1. The simplest design of a piston machine for fulfilling that which is intended by the invention is c h a r a c t e r i s e d in that the machine only has one piston in each cyl- inder, which piston interacting with its cylinder by their mutual design form a working chamber, either a combustion chamber or a compressor chamber, and at least one or two pump chambers interacting with this working chamber, wherein the piston by reciprocation sucks in a charge/charges of which at least one is a supplementary after- charge to the charge/charges supplied at the ordinary suction valve, scavenging port and/or by another/other supply system/systems and may be a supplement hereto of the same or other kind, supplied to the combustion or compression chamber of the combined working and pumping piston itself by being blown through at least one injection port/ports formed in its cylinder wall only for this, the port/ports being placed according to height close to the position taken by the top of piston when the piston is in its bottom dead point and at least so high that it/they become completely exposed by the piston top, whereby there is achieved a piston controlled opening and closing of the injection port/ports determining the geometric opening period which is basis for the temporal period of injection determined by the reciprocation speed of the piston during its passage of the injection port/ports, which temporal injection period in connec- tion with the charging pressure and the flow resistance arising from the feeding of the charge is determining the extent of the aftercharge supplied to the working chamber in the injection period, the latter therefore being the cause of the preferred use of several injection ports that either each or by one annular duct are mutually connected to at least one preferably short exhaust duct connecting them with the dead volume in the pump which compresses the supplementary aftercharge, which dead volume has been minimised, inter alia by establishing the least possible clearance between the pump piston and the bottom part of the pump cylinder, which immediately causes that an unsuitably high pressure on the charge in the pump will arise, which charge has been sucked in through a suitably short injection duct and is retained in the pump by one ordinary, differential pressure controlled check valve disposed in this duct close to the dead volume of the pump, why, for counteracting an unsuitably high pressure formation in the pump, there is associated a receiver with its dead volume and with a vol- ume increasing the dead volume of the pump and the volume of the duct connections extended to the injection ports to a volume implying that the charge is compressed to the pressure which is most suitable for the application of the machine at the φm and load preferred in use, which makes the machine advantageous for functioning in a range only slightly deviating from the m and the load at which it is intended to operate with the associated receiver, but which only by the replacing of this can be adapted to another φm and load range without an unsuitable increase of loss caused by throttling at the intake and loss by compression and injection occurring. 2. A piston machine according to claim 1, c h a r a c t e r i s e d in that the receivers used in the machine are designed so that their individual volumes may be increased or reduced by manual adjustment, or are designed so that all receivers provided in a multi-cylinder machine for its individual cylinders for the same puφose and preferably in the same axis are given an adjustment by an adjusting system for attaining the exact same volume and thus making feasible that the machine, without any other operations, can be adjusted to generate a charging pressure which is suitable for the machine to operate within a certain φm and load range. 3. A piston machine according to claim 1 and partly 2, c h a r a c t e r i s e d in that all receivers used in a machine are designed so that during the operation of the machine and by a suitable supervision by microprocessors, they register the demands on the machine and by computer control they are capable of mechanically, hydraulically, or pneumatically, automatically to adjust up or down the volume content that they are increasing the dead volumes of each pump chamber with, which makes them com- bined receivers and pressure regulators, which without any throttling mechanism associated with its suction duct for limiting the charge flowing to the pump are capable of regulating the charging pressure which is built up in the pump by compression for advancing and injecting the supplementary aftercharging and hereby also the extent of the aftercharge injected into the machine for accurately being adjusted for the most suitable with respect to the immediate φm and load, which is highly important for reducing both the pump losses arising from both suction and compression, furthermore because the regulating ability of the machine makes is specially suitable for applications where it is subjected to varying φms and loads. //: which is the case with an automotive engine, an application, the machine being suitable for in the indicated design, because it can perform aftercharging even from low rpm and because it automatically becomes adjusted to the load requirements that it is subjected to, e.g. caused by speeding up or down, gearing up or down, or by external conditions, such as road inclinations, head and tail wind, if desired even also for the centrifugal forces arising from driving alterations through road bends and from suddenly performed large steering turns, furthermore it is especially suitable for the puφose because the performed automatic regulating operations imply keeping the mixing ratio between fuel and air supply being most suitable for the immediate operating situation, at the same time contributing to a more even driving, both conditions being important for achieving fuel savings and less exhaust pollution. //: 4. A piston machine according to claim 1 , 2 and 3, c h a r a c t e r i s e d in that it uses a traditional crank-connecting rod mechanism for its force transformation and that is pump chamber is formed by use of a step piston with a piston skirt whose diameter is less than the piston crown closing off against the working chamber located above this and also by its larger diameter as compared with the piston skirt closes off down against the underlying, annular pump chamber formed by the diameter difference be- tween the piston skirt and the cylinder wall, through the bottom of which the piston skirt is extended down and reciprocates in the cylinder adapted for its diameter, wherein it seals down against the underlying crank chamber, which embodiment is simple and by its use of known components is easy to manufacture, but because of the lateral pressure on the piston arising from the force transformation and, caused by the contraction relative to the piston crown, the reduced possibilities of the piston skirt for establishing deflection and fastening opportunities for connecting rods of a suitable length and because of the increase weight of the piston compared with a traditional piston results in kind of machine having a relatively great overall height as compared with traditional engine, which in connection with the other drawbacks implies that the machine is only suitable for applications where it runs with moderate and even φm and even load. //: for example as a four-stroke boat, pump, ventilation, and electricity generating engine, or as an air or cooling compressor. //: 5. A piston machine according to claim 1, 2, or 3, c h a r a c t e r i s e d in that it utilises a traditional crank and connecting rod mechanism for its force transformation and that its pump chamber is formed by the use of a stepped piston, the top part of which is formed like a traditional working piston which at its piston crown is sealing against the working chamber situated above it, besides it is formed with an extended piston skirt which at its bottom edge has an outward collaring which at its underside seals against the underlying crank chamber of the machine and which at its upward facing side edge seals up against the annular pump chamber formed between the piston skirt and the pump cylinder, in which annular pump chamber the piston by its reciprocating compresses the charge sucked in to a maximum charge pressure being highest at the moment where the working piston is situated in its top dead point position, which results in that the charge has to be collected and stored while the piston of the machine by its reciprocating from its top dead point toward its bottom dead point performs suction of the succeeding charge and until the piston top by its stroke initiates the exposing of the injection ports formed in the working cylinder and commences injection of the charge previously compressed in the pump, which progress of process suitably is performed in the machine in that immediately after the check valve disposed in the suction duct and the receiver determining the magnitude of the charge pressure and associated with the dead volume of the pump there is inserted a likewise pressure differential controlled check valve in the inlet opening of the exhaust duct immediately before a receiver associated with this duct, the receiver advantageously possibly being a combined receiver and pressure regulator retaining the compressed charge in the receiver until it by the exposure of the injection port/ports by the piston is injected to the working cylinder of the piston, which is a design, though requiring two check valves, implies the advantage of the piston having a greater skirt diameter and in addition, because of the outward collaring of the piston, has an increased lower diameter thus making possible the use of a shorter connecting rod with greater freedom of deflection, but also by its form implies that the annular pumping chamber is isolated from receiving lubrication as it is usually made, which is disadvantageous because the used ordinary crank and connecting rod mechanism results in generating a not insig- nificant lateral pressure on the piston, as well as the increased piston weight makes the machine less suitable for applications implying varying φm. 6. A piston machine according to claim 1, 2, or 3, c h a r a c t e r i s e d in that its pump chamber is annular and formed by interaction between a short and light cylindrical piston without stepping, its cylinder, and a projecting, hollow, and light cylindrical piston rod connected rigidly with the piston, and a cylinder bottom piece with a combined sealing and guide bushing disposed at its centre, wherethrough the piston rod has been passed down into an underlying pressure oil lubricated crank disc cham- ber and attached to a yoke extending peφendicularly to the piston rod and forming part of either a "Scottish yoke mechanism" or of an "I-yoke mechanism", which is the force transforming mechanism and transforms the reciprocation of the piston to rotation or the reverse, as both mentioned mechanisms are advantageous in that they ensure an exact piston reciprocation in the cylinder axis, besides performing sinusoidal (harmonic) piston strokes by evenly performed rotations, which in a simple way makes possible a complete (100 %) outbalancing of all reciprocating masses in the cylinder axis, and for the number of cylinders mostly used also a complete (100 %) outbalancing of the masses moved peφendicularly to the cylinder axis without the use of balancing mechanisms, and besides, what is important for the realisation of the ma- chine, that the "Scottish yoke mechanism" reduces the lateral pressure on the piston rod and the piston to only being 50 % of that generated by a crank and connecting rod mechanism used for the same purpose, while the "I-yoke mechanism" operates without any generation of lateral pressure on the piston rod and the piston, of which especially the piston, being isolated from the crank disc chamber is not supplied with lu- bricating agent herefrom in a suitable manner, has a need for relief of lateral pressure, not the least because it both acts as a piston in the working and pump chamber under thermal load conditions, working conditions counteracted in the machine either by adding a lubricating agent to the charge sucked into the charging pump by fog lubrication to the least practicable extent and which later, by combustion or by its presence in a compressed gas, is the least possible contaminating, or by quite simply using the elimination of the lateral pressure on the piston for completely avoiding lubrication, advantageously reducing the exhaust contamination, either by coating the piston rings, alternatively the piston and/or the cylinder with a film, e.g. as the amoφhous diamond film developed by Sandia Laboratories which can be coated at room temperature, is temperature resistant until 800 degrees Celsius, besides being stress-free, safe against crackles, having a hardness corresponding to 90 % of that of crystalline diamond, be- ing resistant against to almost all chemicals, and, very important for the puφose, having a very low coefficient of friction, or by using light, temperature resistant materials for the piston rings, alternatively the piston and/or the cylinder, having or which may be provided with smooth surfaces, for example of ceramic type, //: which design and materials interacting with automatically controlled, combined receivers and pres- sure regulators make the machine capable of in a hitherto unattainable way to be advantageous, in relation to its developed torque and yield, in being used as a light and compact automotive four-stroke engine or as a single-stage compressor, particularly made like a "boxer" engine with two piston sets per yoke disposed in the same cylinder axis, projecting to both sides of the common yoke, and furthermore as engine be- cause of the supplementary aftercharge to eliminate or limit the need for using in recent times more and more complicated and voluminous top valve constructions with an increased number of valves per cylinder. //: 7. A piston machine according to claim 1, 2, or 5, partly 5 and 6, c h a r a c t e r i s e d in that the piston used in the machine is a stepped piston formed as that described in claim 5 and with a receiver arrangement also as described in claim 5, but which deviates from this machine by the traditional crank and connecting rod mechanism being substituted by a "Scotch yoke mechanism" or an "I-yoke mechanism" as described in claim 6, which causes that the drawback mentioned for the machine in claim 5 con- cerning the need for lubrication of the piston parts situated in isolation above the outward collaring is eliminated for the machine used as compressor or four-stroke engine, partly by the lateral pressure on the piston either is reduced or eliminated and besides that by crank disc chamber can be made pressure oil lubricated and thereby lubricated the lowermost cylinder wall and is flung up against the underside of the piston which is advantageous for the conducting away of heat from this, but makes impossible to use the machine as two-stroke engine. 8. A piston machine according to claim 1 to 7, c h a r a c t e r i s e d in that it is made either as a two-stroke or a four-stroke engine, which, irrespectively whether the supplied aftercharge air is compressed in a pump chamber making possible an immediate supply or requiring an intermediate storage before the supplying to the working cham- ber, is made with a receiver arrangement as described in claim 5, but elaborated in that between the receiver which suitably is an automatically controlled, combined receiver and pressure regulator, and the injection port/ports there is disposed a rotary valve, the rotation of which is synchronized to follow the φm of the engine and be geared to rotate with a φm being the same or half of this φm, besides being shaped with a duct system suitably extending on the cylindrical periphery of the rotor and here by its polar angle extension and its placing is capable of within the period where the piston has exposed the injection port/ports to control the moment in relation to the position of the piston where the duct opens the connection between the receiver and the injection port/-ports and hereby initiates injection of the supplementary aftercharge by a simul- taneous down blowing of the pressure of the charge stored in the receiver, which injection and down blowing is continued until either the duct connection is closed or the piston closes the injection port/ports by its movement up from the bottom dead point. 9. A piston machine according to claim 1 to 8, c h a r a c t e r i s e d in that the ma- chine is a two-stroke engine with a receiver and rotary valve arrangement as described in claim 8 with a rotary valve synchronised to rotate with the same φm as the engine, and that the engine besides that is provided with scavenging and exhaust ports together with injection port/ports which because of the performed control of the moment for injecting by the rotor without having any inadvertent influence on the progress of the process in the engine, is made at a level somehow above the opening of the exhaust port, and the rotary valve is designed with a duct system with a relatively large through cross-section which immediately after the piston having covered the opening of the exhaust port during its reciprocating from the bottom dead point, abruptly opens and quickly shuts the injection of the aftercharge which because of the very short in- jection period has been imparted a charging pressure needed for this, which arrangement results in that the engine gets a particularly suitable high degree of filling. //: As the charge in engines with direct fuel injection is atmospheric air, which, if necessary for lubrication of the isolated piston part, may be supplied with a small oil fog content, and in engines with indirect fuel supply, either established by a fuel injection system associated with the supply duct of the aftercharge pump or a carburettor allowing the charge to be a suitable mixture of air, fuel and oil. //: 10. A piston machine according to claim 1 to 8, c h a r a c t e r i s e d in that the machine is a two-stroke engine designed with a rotary valve like the one described in claim 8, but different from this in that it is made throughout with several injection ports disposed in a location high in the combustion chamber of the engine and mutu- ally connected with a suitably designed connecting duct situated in the cylinder block and/or on external side of the cylinder lining associating them with rotary valve placed between them and receiver established for intermediate storage of charge, as the injection ports are designed so that they both direct the charge supplied by injection up against the cylinder head of the engine and imparts a suitable turbulence to the sup- plied charge, and as the injection is controlled by the ducts of the rotary valve synchronised for the piston position and formed in its cylindric periphery, which at their placing and in their course are given such a design of the width and the depth that they gives the injection a characteristic causing that the injecting of the first part of the charge is initiated immediately after the initial outflow at the end of the work stroke by the piston has been performed in the period from its exposure of the exhaust port to its exhaust of the scavenging port and is continued with a relatively limited down blowing of the charge pressure through the whole scavenging period and until the piston during its reciprocation from the bottom dead point blocks the exhaust port, whereafter the residual pressure on the charge is abruptly blown off as an aftercharge, which causes a scavenging which, like longitudinal scavenging, is advantageous for the exhaust of residual gasses and for achieving the best possible charge with fresh air before starting the subsequent combustion of a fuel charge supplied by direct injection. 11. A piston machine according to claim 1 to 8, c h a r a c t e r i s e d in that the machine is a four-stroke engine with a receiver and rotary vent arrangement as described according to claim 8 with a rotary valve synchronised to rotate with an φm which is half of the engine, which rotor designed with one duct, or with two ducts, which at their extension on the cylindric periphery of the rotary valve and by the synchronisation of the rotor, designed with one duct, is capable of suitably supplying a charge, either only as a cooling medium after the end of a work stroke, or only as a really supplementing aftercharge after the end of a intake stroke, and even more suitably designed with two ducts to deliver a certain part of the intermediately stored charge in the receiver as cooling medium and the remaining part as a really supplementary after- charge, as the distribution of the totally available charge to the two different puφoses can be freely determined by designing the two for the control of the supply ducts with a mutually different extension on the cylindric periphery on the rotary valve. 12. A piston machine according to claims 1 to 11, c h a r a c t e r i s e d in that in the machine designed with several cylinders in line there may be used rotary valves placed on a common shaft where they are polarly angularly turned relative to their function uniformly performed for each cylinder, so that the function is performed correctly in relation to the piston reciprocation in each cylinder, as their common shaft is rotated with an φm adjusted to the intended function and has been given its drive taken independently from the crank disc shaft of the machine, which because thereof can be added an φm or centrifugally controlled mechanical, hydraulic, or electronic displac- ing mechanism capable of performing a relative turning between the rotor shaft and its driving wheel, whereby in relation to the rpm of the machine while running, in machines where initiation and terminating injection of charge are only determined by the duct design of the rotary valve, there may be achieved a suitable displacement of the times for initiating and termination of the injection of the aftercharge, or in machines where the rotary valve only determines the time for initiating the injection and the injection port/ports at their vertical location in the working chamber, and by the covering by the piston of it/them determines the time for terminating the injection, there may be achieved a varying of the length of the injection period, which is of the greatest significance for accommodation to a direct fuel injection which by application of modern technology, e.g. as of FICHT, also may be controlled to vary both the injection time and the amount of fuel supplied to the machine depending on its momentary φm and load while running. 13. A piston machine according to claim 1, 2, 3, 7, 8, 9, 10, 12, or 8, partly 5 and 6, c h a r a c t e r i s e d in that the machine, besides its working chamber, has two pump chambers formed by an interaction between a piston and its cylinder as described in claim 5, but deviating in that the piston is associated with a force transformation mechanism which is either a "Scottish yoke mechanism" or an "I-yoke mechanism" as described in claim 6, and the cylinder has been provided a bottom part with a combined sealing and guide bushing provided for the passing through of the piston rod, which causes formation of a further pump chamber besides that formed at the outward collaring of the piston, implying that the machine in a special application of the two pump chambers very suitably can be used as a two-stroke engine or as a threestroke compressor, as the machine as two-stroke engine uses the pump chamber situated under the collaring of the piston as scavenging air pump and the pump chamber situated above the collaring of the piston as a pump for aftercharging, possibly besides also for the making of pressurised air for a pressurised air controlled, direct fuel injection (as used by ORBITAL), which division of application puφoses is particularly suitable in that the pump chamber under the collaring has a pump volume greater than the working chamber of the piston itself and thereby is capable to deliver a suitably large scavenging air volume which, consisting of pure atmospheric air, causes an improved scavenging, furthermore is advantageous by not increasing the exhaust through its exhaust port or exhaust valve by a content of fuel, therefore prevents consequential fuel loss while at the same time the exhaust gas is kept free from supply of incompletely combusted fuel, the latter being significant because the engine has been given a controllable direct fuel injection system (e.g. as of ORBITAL or FICHT), furthermore is given combined receivers and pressure regulators for both the scavenging air pump and the aftercharge pump which suck in their charge through a common intake opening dividing into two individual supply ducts, each with their pressure differential controlled retaining check valve disposed close to the scavenging and the charge pump, respectively, the latter being further associated with a rotary valve displacing the aftercharging to take place to the combustion chamber of the engine after the termination of the exhausting herefrom, which arrangement making possible that the engine while running is capable of automatically regulating the performed supplies of scavenging and aftercharge air in the progress of the process together with fuel to be the optimum for carrying through the most economical and least polluting running. 14. A piston machine according to claim 1, 2, 3, 7, 8, 9, 10, 12, or 13, partly 5 and 6, c h a r a c t e r i s e d in that the machine is a two-stroke engine designed as described in claim 13, but designed in that the scavenging air pump and the charge pump has been given each their intake opening, which makes it possible to perform individual and different charge sucking in to the two pump chambers, for example an air and lubrication mixture, or an air, fuel, and lubrication mixture for the aftercharge pump, while the scavenging air pump sucks in pure atmospheric air, which differentiation can be suitable for certain embodiments of the engine. 15. A piston machine according to claim 1, 2, 3, 7, 8, 9, 10, 12, 13, or 14, partly claim 5 and 6, c h a r a c t e r i s e d in that the machine is a two-stroke engine designed as described in claim 13 or 14, but designed in that from the dead volume of the charge pump one or more duct connections extend, reaching the piston close to its top dead point, by the circumvention of the collaring of the piston short-circuits between the dead volume of the charge pump and the chamber of the scavenging air pump, which implies that the charge pump is blown off of its present very high pressure and by the blowing off of this increases its ability to quickly initiate a new sucking in after the reversion of the piston over the top dead point, further implies that the charge sucked in to the scavenging pump chamber is supplied from the charge pump to the scavenging air pump as an aftercharge, as this pump just at the time of supply has finished its own sucking in of charge, where by the described arrangement there is simultaneously achieved an enhancing of the pump efficiency of both pumps. 16. A piston machine according to claim 1, 2, 3, 7, 13, or 15, partly claim 5 and 6, c h a r a c t e r i s e d in that the machine is a three-stage compressor using the same piston, piston rod and cylinder design as described in claim 13 and one of the force transformation mechanisms described in the same claim, but utilizing the 3 pump chambers found in the machine in another way than by its use as engine, in that though the pump chamber situated under the collaring of the piston by the reciproca- tion of the piston is used, by one like the supply duct designed for engines having a pressure differential controlled return flow blocking check valve placed close to the dead volume of the pump, to suck in and perform a first stage compression of a charge which, during the reciprocation of the piston from its top dead point, is forced out to a duct connecting the first stage pump with the dead volume of the second stage pump chamber through a pressure differential controlled check valve disposed close to the dead volume of the pump, as the charge before supplying to the second stage pump chamber passes a further pressure differential controlled check valve provided in the supply duct close to the dead volume of the second stage pump over the piston top, as the piston performs its sucking stroke to the second stage pump simultaneously with the first stage pump performs its compression stroke, which two pump strokes are finished at the reversal of the piston over the bottom dead point and at the reciprocation of the piston against the top dead point are succeeded by the first stage pump sucking in a new charge and that the second stage pump compresses the charge previ- ously received from the first stage pump, respectively, which hereby is forced to exit the pump through its exhaust duct branching off from the dead volume of the second stage pump and having a pressure differential controlled check valve provided closely to the dead volume of the pump, in order to be transferred to a receiver temporarily storing the charge until the piston after the subsequent reversal over its top dead point begins its sucking in to the third stage pump chamber which is the annular pump chamber formed by the interaction between the stepped piston and its cylinder, and from the receiver through a pressure differential controlled retaining check valve disposed closely to the dead volume of the third stage pump until pressure equalisation has been achieved, is transferred to subsequent compression in the third stage pump and, after being imparted its maximum pressure, is forced herefrom to be transferred to an associated larger pressure vessel in a traditional way through a pressure differential controlled and retaining check valve, ensuring equalising of the pressure pulses caused by the pump strokes of the compressor and at the same time by its magnitude makes possible a lesser pressure variation and longer pauses between stop and re- newed start of the compressor, the pump efficiency of which besides may be improved by establishing one or more short-circuiting ducts that may function as described in claim 15. 17. A piston machine according to claim 1, 2, 3, 6, 7, 8, 9, 10, 11, 12, 13, 14, 15, or 16, c h a r a c t e r i s e d in that in connection with the use of either a "Scottish yoke mechanism" or an "I-yoke mechanism" it is provided a light and hollow cylindrical piston rod which in order to improve the conducting away of the heat from the piston, like strongly heated exhaust valves, are filled with sodium melting at a relatively low temperature and which as a liquid by the reciprocation by the piston and the associated piston rod is suitably flung to and fro in the hollow piston rod and hereby fulfils the intended puφose.

Inventors: RASMUSSEN GUNNAR VESTERGAARD, RASMUSSEN, GUNNAR, VESTERGAARD
Applicants: RASMUSSEN GUNNAR VESTERGAARD, RASMUSSEN, GUNNAR, VESTERGAARD
Application year: 1999
Main classification: F02B33
IPC codes: F02B33, F02B75, F02F1