DE3233391A1 - Engine and accessories, in particular carbon-fuel engine - Google Patents

Abstract

The invention relates in particular to measures for making the pressure and the temperature in the external firebox of a combustion chamber, fed by a compressor set, between compressors and expanders so high and at the same time keeping the whole engine or the combustion installation operationally reliable, that solid fuel also, for example in rod form, can be burnt in the high temperature at a given advance speed of the fuel rod. The temperature can be brought so high that the fuel rod being inserted ignites and burns itself. Gas which is too hot after combustion can be cooled economically by water injection and used for work power output. In the implementation of the invention, it emerged that such engines with external fireboxes, as a result of good compressors, valves and the combustion chamber design, can also work as petrol engines with degrees of efficiency which are not inferior to those of existing Otto engines. Fuel powder can also be burnt and the parts, which serve for perfecting the engine, can find further applications in hydraulics and pneumatics, as well as in aeroplane construction and vertical take-off of aerofoil aeroplanes. As the expanders in such engines produce work on every downward stroke, the engines are particularly compact or they produce increased power for their weight and dimensions.

Description

ENGINE AND ACCESSORIES, IN PARTICULAR

CARBON FUEL ENGINE.

The invention is based on the object of a racing room system create, especially for internal combustion engines with external combustion between Compressors and relaxers is suitable and especially direct separation from states or from solid fuels, for example, purified coal, allows.

The solution of the task is for plants according to the genus of the generic terms of claims 1 and 2 by means of the features of the characterizing parts of Claims 1 and 2 solved.

Particularly advantageous developments of the task are after characterizing parts of claims 3 to So solved.

The solution also includes designing the compressors so that one constant supply of highly compressed air is ensured, which causes self-ignition and self-combustion of the solid fuel rod in the combustion chamber enables and ensures. The compressors are provided with dead space-shaped molds and valves and that hot fuel gas may be used for water evaporation injected water so that the Relaxers - working parts can work at sufficiently low temperatures. With the internal combustion engines of the invention, the dependency = gigknit of electricity generation g and the vehicles are reduced or switched off from gasoline and the burning systems should make heating systems independent of heating oil.

Figure 1 is a longitudinal section through an Urennraum arrangement of the invention Figure 2 is a section through Figure 1 along part of the line II-II.

FIG. 3 is a section through FIG. 1 along the line III-III, FIG 4 is a section through FIG. 3 along the line IV-IV.

Figure 5 is a section through Figure 4 along the line V-V.

Figure 6 is a section through another assembly of the invention.

Figure 9 is a section through part of an alternative thereto.

Figure 7 is a cross-section through an arrangement of the invention.

FIG. 8 is a section along VIII-VII through FIG. 7.

Figure 10 is a longitudinal section through part of a compressor according to the invention, and Figure 11 is a longitudinal section through a nozzle arrangement the invention.

Fig. 12 is a longitudinal section through an aggregate of the invention.

Figure 13 is a section through Figure 12 along the line: A-A.

FIG. 14 shows the housing of FIG. 12 in a separate representation.

FIG. 15 shows the piston of FIG. 13 in a separate illustration, FIG. 16 is a section through Figure 15 along the L-line B-B.

FIG. 17 shows part of FIG. 12 in a separate demonstration, FIG. 18 Figure 17 is a section through Figure 17 along the line C-C.

Fig. 19 is a longitudinal section through an aggregate of the invention.

Fig.20 is a longitudinal section through a piston of the invention.

Figure 21 is a section through Figure 20 along the line A-A.

FIG. 22 shows the piston of FIG. 20 in a separate illustration.

Figure 23 is a view of Figure 22 in the direction of the arrow: B.

Figure 24 is a section through Figure 23 along the line F-F.

Fig.25 is a longitudinal section through a piston shoe of the invention.

FIG. 26 is a cross section through the center of FIG.

FIG. 27 is a top view of the shoe of FIG. 25.

Fig. 28 shows part of the invention in a view from the side.

Figure 29 is a section through Figure 28 along the line A-A.

Fig.30 is a longitudinal section through parts of the invention.

Figure 31 is a cross-section through Figure 32 along line B-B.

Fig.33 is a longitudinal section through a housing part of the invention.

FIG. 34 is a section through FIG. 33 along the vertical dash-dotted line Line in Figure 33.

Fig. 35 is a section through Fig. 34 along the line D-D.

Fig. 36 is a section through Fig. 38 along the line B-B.

Fig.37 is a longitudinal section through a piston of the invention.

Fig. 38 is a longitudinal section through a piston of the invention.

Fig. 39 is a longitudinal section through a piston of the invention.

Fig.40 is a longitudinal section through an engine of the invention.

Fig.41 is a longitudinal section through an engine of the invention.

Figure 42 is a cross section through part of the invention.

Fig. 43 shows the same part with the valve revolved.

Fig. 44 is a longitudinal section through a valve of the invention;

Fig. 45 is a longitudinal section through an engine of the invention.

Fig. 46 is a longitudinal section through a motor of the invention Fig. 47 Figure 46 is a cross-section through Figure 46 along line F-F.

Figure 48 is a view of part of Figure 46 from above.

Figure 49 is a view of part of Figure 48 in the direction of the arrow above figure 48.

Fig. 50 explains mathematical relationships.

Figure 51 is a section through Figure 52 along the line A-A.

Fig. 52 is a longitudinal section through an engine of the invention.

Within the figure there are excerpts with the letters are provided, which carry the arrows of the cutting = lines through the parts of the figure are seen, Fig.53 is a longitudinal section through part of the invention.

Fig.54 is a longitudinal section through part of the invention.

Figure 55 is a cross-section through Figure 54 along line B-B.

Fig.56 is a longitudinal section through part of the invention.

Fig. 57 is a longitudinal section through part of the invention.

Fig.58 is a longitudinal section through a valve of the invention.

Fig. 59 is a section through Fig. 58 along the line B-B.

Fig. 60 shows a diagram of the engine of the invention.

Fig. 61 shows a diagram of the engine of the invention.

Fig. 62 shows a diagram of the engine of the invention.

Fig. 63 shows a diagram of the engine of the invention.

Fig. 64 is a cross-section through a prior art motor.

Fig. 65 is a longitudinal section through an engine of the invention.

Fig. 66 is a cross section through an engine of the invention.

Fig, 67 is a longitudinal section through an engine of the invention.

Fig.68 is a longitudinal section through an engine of the invention.

Fig. 69 is a cross section through an engine of the invention.

Fig.70 is a longitudinal section through an engine of the invention.

FIG. 71 shows a view from above into FIG.

Fig. 72 is a longitudinal section through a cylinder of the invention, Fig. 73 is a longitudinal section through an arrangement of the invention.

FIG. 74 is a diagram of the engine of FIG. 72.

Fig. 75 is a longitudinal section through a motor of the invention.

FIG. 76 is a diagram of the engine of FIG.

Fig. 77 is a section through a crankshaft of the invention.

Figure 78 is a section through a pumping element of the invention.

Fig.f9 is a longitudinal section through a piston of the invention and Fig.80 is a methematic representation of the geometry of the Flow figures 1 and 5 show a section through the schematic of an exemplary embodiment of my invention of a solid fuel rod in an air or gas-burning engine or, in general, a solid fuel combustion device. The housing of the combustion chamber is denoted by 10 and it contains the prechamber 7 which, through the feed line 8, contains a gas, in the internal combustion engine preferably air with little or no other gas components. The gas or air is supplied under sufficiently high pressure through the inlet 8 into the front chamber 7. With internal combustion engines it is preferred to compress the air in several chambers, compress it one after the other in different chambers, so that finally an almost continuous, if somewhat fluctuating, compressed air or compressed gas flow through the inlet or the inlets 8 in the antechamber 7 of the combustion chamber is pressed into the combustion chamber body 10.

At the same time, a solid fuel rod, denoted by 4, is used is, through the fuel rod guide 1, which contain a cooling chamber 2 with wall 3 like, passed into the flame chamber or to the flame point 5. It flows at the same time an adequate amount of gas, but preferably compressed air from the antechamber 7 through the directional concentration and guide nozzle 6 approximately in the direction of the arrow 11 to the focal point 5 and meets there on the rod made of solid fuel. Of the Solid fuel may be cleaned and pressed coal, for example.

When the air flow from the nozzle (s) 6 and the fuel meet fabric rod 4 from guide 1 in the flame chamber or the combustion point 5 burns Fuel of the rod 4 in the air coming from the nozzle 6 on the tip of the fuel rod 4 flows in. The ignition duration of the fuel at point 5 can, for example then that happened in the rear parts, for example in the after-chamber There is a high temperature, which is higher than the inflammation or flame tempe: The temperature of the fuel is 4 and this high temperature can be seen in the combustion point 5 propagates into it or is permanently present in it. Another possibility is the ignition of the fuel by means of specially arranged, man-tired ignition devices or ignition means.

However, I prefer the air in the compression chambers compress so high that the temperature of the compressed air passing through inlet 8 flows into the antechamber 7, higher than the ignition temperature of the solid fuel 4 is.

For example, if the solid fuel 4 consists essentially of purified, firmly pressed coal, then the self-ignition temperature is between 200 and 500 degrees Celsius. With solid coal it is usually around 400 degrees.

Therefore I prefer to compress the air to around 25 atmospheres and under this pressure via the inlet 8 approximately continuously into the antechamber 7 to channel in. The air is then so hot when flowing through the nozzle (s) 6, that the coal fuel 4 burns in it immediately.

Since the incoming air also has a high concentration of oxygen has, the self-ignition temperature of the solid fuel 4 usually falls significantly below the ignition temperature valid for pressureless atmospheric air. That is why I use a lower feed pressure in some execution examples in the air, than 25 atmospheres. The fuel rod 4 is either in the guide 4 fitted so that the pressure from space 7, 20 does not come from the combustion housing 10 can escape, or a seal is provided that the fuel rod 4 seals in the guide 1 in the direction opposite to the focal point 5. Finally, it is still possible to completely store the fuel 4 in a chamber, which contains the same pressure as chamber 7, 9 or 20 to prevent undesired escape of pressure, gas leakage from the spaces in the combustion chamber body 10 to avoid.

As known from my earlier patent applications and other literature is, the burned or burning fuel-air mixture flows at the end of a combustion chamber 20 Via a discharge into the relevant expansion chamber, the expansion chamber or di <3 I; ntspanncrkaniern to do the work including the drive of the Compressor to deliver.

Correspondingly, this flows in the combustion in the flame place 5 further heating and expanding gas, e.g. Fuel-air mixture, for example through channel 21 into the post-chamber 20. There the burn settles lort, in case it has not yet taken place completely in the r3rennplutz 5. Of the Room 9 may serve as a gas cushion room to avoid irregularities in the inflow of compressed air from In: let 8 or inconsistency of the temporal amount of burning and to cushion the temporal combustion pressure, i.e. to reduce fluctuations, thus to act as a kind of accumulator.

I prefer to compress the air so high that it is compressed a little higher in the antechamber 7 and there is a somewhat higher pressure in it than in the post-chamber 20. This creates a constant flow from nozzle 6 along arrow 11 on the staendi, g an urgent ol Fuel rod 4 with constant combustion with ignition in the combustion place 5 and a constant flow through channels 21 into the post-chamber 20 is achieved. The pressure difference in the chambers 7 and 20 has an influence on the combustion rate and the flow rate, further influence on the combustion and flow rate is given by the pre-value rate 12 in the direction of the arrow 12 of the fuel rod 4. This fuel rod is therefore more preferably stolted in vehicle engines = we; sc in its speed in the direction of arrow 12 controllable. For example, the speed in the direction of arrow 4 is controlled directly or indirectly with the accelerator pedal, the cruise control of the vehicle. This can be done, for example, by means of a regulating pump that directs a time-varying amount of pressure fluid against the thrust device 15, which then drives the rod 4 faster or slower in the direction of arrow 12 according to the amount of fluid, with the whole motor then running faster or slower. Instead of a fluid drive, however, an electrical or mechanical drive, if necessary with a speed controller for the advance of the fuel rod 4 in the direction of arrow 12, can be used.

One of the main reasons why I really want to, a slightly higher pressure in the pre-chamber 7 than in the post-chamber 20 is that there is no complete combustion of the substance of the fuel rod 4 7tlerr (1iChe. This is intended to avoid toxic exhaust gases or to reduce the toxic content of the exhaust gas through incomplete combustion.

The focal point 5 therefore preferably has such a geometrical one Form and dimensioning that the hot air jet from nozzle (s) 6 feeds the fuel 4 fully burns and flowed.

The cross-sections and speeds of arrows 11 and 12 are intended therefore stand in a certain relation to one another or within one another of a certain ratio range. This ratio or this The ratio is also, for example, also from the printing height in room 7 or Depending on room 20, for example, if you have the same cross-section of the nozzle (s) 6 and the fuel rod (the fuel rod) 4, then to get a very rough look to give the speed of the hot air flow 11 in nozzle 6 at about 25 bar Pressure about 1280 times faster than the forward influence movement 12 of the fuel rod 4 is. At about 50 bar pressure in the hot air it is for complete combustion the speed of the hot air through nozzle 6 is about 800 times faster, ats the Inset Be movement of the fuel rod 4. These figures are However 'only very rough, very preliminary and can still make further corrections After further research and measurement, it is now still subject to expect that the combustion in burner place 5 cannot be complete enough, if it is not ensured that the hot air jet 11 from nozzle 6 after combustion of the outer part of the fuel rod 4, also the inner or lower, rear parts of the fuel rod 4 supplied with fresh hot air so that the entire thickness of the rod 4 burns in the air.

Therefore, according to FIGS. 3 to 5, there are often several fuel rods 4, such as 24, 34, 44, 54 arranged in guides 1 and supplied. taking them into the hot air supply air Push 26,36,46,56 in from the hot air nozzles. The hot air flows here through nozzles 26,36,46,56 along the arrows drawn therein in FIG relevant fuel rods 24,34,44,54. A correct and complete combustion to get = hold, the cross-sections of the supply lines 1 of the fuel rods and the thickness of the fuel rods 4 etc. dimensioned so that the thickness of the hot air nozzles 6,26,36,46,56 a certain thickness 19 (height of the nozzle compared to its width) compared to the thickness 18 of the relevant fuel rod 4,24,34,44,54. Because when the thickness 19 of the nozzle 6 is reduced compared to the thickness 18 aes Fuel rod 4 increases the speed according to arrow 11 of the hot air. Of the The hot air jet then has a stronger penetration - or penetration - depth to the full Meet all places and parts of the fuel rod 4,24,34,44,45. Means 5 more correct Choice of the supply pressure of the compressed air and the ratio 19 to 18 the relative thicknesses of these and the fuel rod along with the correct dimensioning the rate of advance 12 of the fuel rod is the combustion in the burner place 5 influenced very far. The correct mastery and knowledge of these relationships together with the mastery of the construction of suitable compressors for sufficient high hot air pressures result in the realization of a good or a less good one solid fuel engine of the invention.

The shape, cross-section change and direction of the spaces canals e 9,7,5,6,21,20 depends largely on the speed at which the engine is supposed to work dependent and so on the pressure.

In the case of complete combustion and work the engine without high Excess air, i.e. in the case of a high-performance process in a small one Machine as an internal combustion engine, is due to the high pressure of the incoming, compressed hot air, the maximum combustion temperature at focal point 5, Channel 21 and post-chamber 20 very high. It can or would become so high that conventional metals if they are; Form body 10 of the burning device, narrow 5 zen would. In addition, these high temperatures can affect the, die1 relaxer be disadvantageous in that the burnt gas flows off to produce the known To do expansion work. This is especially the case when these relaxers traditional Bauert, for example cylinder with oscillating pistons made of metal are.

So I recommend going to channels 21 or chamber 20 to those Places where combustion has just ended in the flow, or near or after this point, water under high pressure as a fine mist, for example through the Due = se (n) 13 along the arrows 14, inject. The amount of water injected should be in my engine as much as possible be dimensioned so that the water is converted into steam and the gas-air-steam mixture there is no more water when it emerges from the expansion tank, but rather it contains steam, which is still a little overheated, for example by 5 to 35 degrees, so that the steam and that The escaping gas is not too humid to cause rusting. The high pressure pumping means for fine dusting of the water during spraying can be found in parallel patent applications according to the inventor's designs. Details about water - injection quantities, Devices, times, etc., as well as about the relationships around the focal point 5 one in corresponding Rotary Engine Kenkyusho reports, which are delivered with the purchase of the license can be. What is achieved with this water spraying process is that the later Temperatures in the relaxer or in the relaxers stay low in order to be portable the high combustion chamber pressures described for direct solid fuel = combustion to allow and thus to realize a highly effective engine.

At atmospheric pressure, for example, water vapor is around sixteen = hundred times the volume of water. With the correct amount of water injected, it is possible the engine as if it were working with air fuel gas, but at lower temperatures allow.

FIG. 1 also shows that a rotating drum 22 is in the combustion chamber 20 can create a rotating liquid bath in which the cool = liquid (e.g. water) 23 circulates. Through holes 24 like a dosed, So a limited amount of such coolant from the rotating liquid bath or a correspondingly more stationary liquid bath to cool the wall of the body 10 may escape.

this is another way of preventing overheating and breakage of burner parts. The arrangement of Figure 1 is a body that contains spaces. In spite of this, the expression "Brenn = kourpor" has not yet become established. One calls such a device as that of Figure 1, which one can screw or connect to a set of compression chambers and a set of expansion chambers, allcme in "Combustion chamber" and an internal combustion engine that conducts air from compressors through such an arrangement to a set of expansion working chambers, an internal combustion engine with external combustion. If in the literature or in this patent application the term "combustion chamber" is written, then this is either one of the spaces in a body 10 or the body 10, which contains the real combustion chamber 9, 7, 21, 20, is simplicity In FIG. 2 it is visible how the fuel rod 4 lies exactly in front of the fuel rod guide 1 when it is fed to the combustion chamber arrangement 10 in the fuel tank. To the right and left or only to the right or or only to the left of it are the fuel rods 16 of the same fuel = 4-tab layer in the tank. The fuel rods of the next fuel rod layer 17 then lie on top of this in the tank. So you can fill the fuel tank with full space utilization with fuel rods 4,16,17 and one after the other at the appropriate time to the fuel rod guide 4 by means of the thrust device 15 and the feed in the guide 1 of the soot combustion chamber arrangement 10 according to arrow 12 perform at speed 12.

Figure 6 shows a longitudinal section through a compressor or expander for particularly high temperatures. If namely the motor according to Figure 1, other figures or other patent applications at the inventor's idea with very high pressure without cooling; If solid fuel residues remain, then conventional compressors and expanders of engines or the cylinders and pistons of Otto engines or diesel engines may be unsuitable for withstanding the high temperatures. According to the invention, the Merkoemmliche Kotben made of metal is therefore in Figure 6 by a piston made of water or a other cool liquid replaced.

FIG. 6 therefore shows the compression chamber 27 in the compression chambers Housing 25. The compression chamber is, however, an expansion chamber if the unit works as a relaxer. And it's a suction - compression - expansion - and Exhaust chamber if the unit works as a gasoline engine or as a diesel engine.

Below the above-mentioned Gehoeuses 25 is a ring element - Amrd.

tion, for example, according to the patent application P 32 26 069.5 of July 13th Arranged in 1982. In this special case it consists of the ring element pairs or Elements 33 and 35, one of which rests on the reciprocating piston 37 and against it Head is sealed. The element at the other end of the element set 33,35 seals opposite the housing 25. A chamber is thus within the ring elements 33, 35 formed, which is in communication with the chamber 27 and is filled with water, which forms the water bulb 40 of the invention. Below or on the reciprocating piston 37 is the reciprocating piston drive 38,39 arranged, which is the connecting rod of a crank = shaft machine or the piston shoe of a piston shoe - hoist - machine may be. Through the Piston stroke drive, the ring elements 33, 35 are periodically tensioned or relaxed. For the practical construction of the ring elements and the ring element set, such as the chamber therein, it is appropriate, the rules and formulas of the patent application mentioned dated July 13, 1982 to be observed. Because otherwise the thing will not work and the elements break. FIG. 6 shows the elements in the relaxed state. By regulator, For example, the bore, 28 becomes the chamber within the elements 33.35 now Filled with water, refilled or wX excess water or liquid emptied, so that the water level 40 shown in the drawing is approximately at the level of the Arrangement, regulation 28 is reached. Thereafter, the control 28 is closed, what can be done with known means, cock, valve or the like. After that drifts the piston stroke drive 38,39 upwards the reciprocating piston 37, the elements 33,35 axially be compressed, this lifting process is set until the water or 4 forms the liquid 40 in space 27 and the desired compression valve Opening pressure reached. Has that happened or is the exhaust valve otherwise has been opened, then the outlet valve 29 opens and lets the compressed Air escapes through chamber 41 and conduit 31 or directs the compression -Air over the mentioned ways 29,41,31 with further compression or thrust stroke out of the chamber 27 into the channel 31. Is an automatic pressure control the opening of the valve 29 is provided, then the passage room can 41 partially or fully filled with cool liquid, for example with water because the system can be dimensioned in such a way that the air flowing through a lowering of the Kuehlwa = users from room 41 in room 27 are prevented from entering.

During the following intake hood, the piston stroke drive 38, 39 releases the reciprocating piston 37 sink, which is supported by tension in the elements 33,35 can.

If the arrangement of Figure 6 is used as a Otto engine, then they are also provided with a spark 43. However, if it is a diesel engine, then it is it has a fuel injection nozzle or arrangement 45. The is accordingly Stroke of the water piston 40 is relatively shorter or longer in order to compress the air or the fuel-air mixture in chamber 27 below the self-ignition temperature -rature, as in a gasoline engine, or to maintain the temperature by compression to the temperature level above self-igniting, as with diesel Engine. The stroke of the lifting drive device 38 must then be designed accordingly and to measure the axial compression and relaxation of the ring elements 33 and 35 to be designed accordingly.

As a result of the internal self-cooling within the chamber 27 by the Water from the water piston in it, then this engine higher pressures than the diesel engine allow. However, it should be noted that the lifting speeds are too high advantageously avoids the splashing or splashing of the water piston 40 by mass forces and speed digkedten or to avoid this phenomenon or the possibility to restrict one.

The unit of Figure 6 is intended as an expander at very high temperatures work, then you either let the cool liquid, e.g. the water, out the flow chamber 41 out, Or one sets a channel 47 to the side and mounted the head of the body 25 in reverse so that the valves 29 and 30 point down. This is shown in principle in FIG. For cooling the hot chamber 42 can then be filled with cooling fluid. The hot gas for the expansion work then flows through channel 31 and chamber 4 through their cooling fluid through via Einalssventil 30 in the expansion chamber 27 in. It has to Exhaust valve 29 must be kept closed and only to the exhaust pipe be opened.

Since the exhaust stroke has colder gas than the filling stroke, it is then in Chamber 41 a cooling fluid filling is not always necessary. But it can be arranged by placing an upward curve over the water level at outlet 32 attaches extended exhaust pipe.

Figures 7 and 8 are essentially a lavender repetition of the figures 23 and 25 of the original application P - 31 35 675. However, they extracted some essential points Improvements and extensions of the original invention. This is first once the arrangement of the important inlet valve 80 in the piston head 40 of the piston 26. The pistons 26 are, as is known from the main application, in the cylinder = dern of the housing 8 radially movable. As known from the main application, you are provided with the piston heads 40, the shape of which is designed so that-during the inward stroke of all pistons in the end position, the pistons with their piston heads 40 have a residual space 15, which is almost zero in volume. In practice the dimensions according to the Figu = ren 7 and 8 is this remaining space after full compression, so the action space about half of a hundredth of the total intake and compression volume the figure nei the approximately 160 to 170 mm outer diameter of a housing around the unit around this system of the figures would have etqa 56 cc intake and compression volume. At twice the size, 1: 2 in size, the housing was considerably enlarged about 330 to 340 mm outside diameter and the unit on suction and compression -Volume from around 400 to 450 cc per revolution. With four such aggregate gates axially one after the other about 1600 to 1800 cc per revolution.

The main application lacks a graphic representation and special Description of the path of the intake air in this unit.

According to the invention, therefore, the head 40 of the piston in question 26 is provided with an inlet or suction valve 80. The piston r head 40 has therefor a cavity 84 which extends from the hollow piston part with cavity 86. In addition, the piston head 40 has the suction or inlet valve guide 82 with it the Durchstromknalelen 83 and the guide 82 is used for guide or bracket of the valve stem 8 of the inlet valve 80. A limitation part 1 87 can be arranged be in order to limit the maximum axial movement of the valve 80 in the piston head 40. The inventive purpose of arranging the inlet valve within the Piston or the piston head is a smallest dead space of the cylinder without interference by means of an inlet valve, so that at the 7ylinderspitzsl only the outlets 77,78,79 remain for forwarding into the conveyor channels 77, with the smallest dead space is achieved. The unit is therefore the largest in the situation Amount of compressed gas of high pressure to be delivered efficiently. The introduction of the air or of the gas takes place by opening the valve 80 during the suction or intake stroke of the the piston concerned or the entire piston 26.

It is advisable to fill the housing with a form, for example by means of a turbocharger to achieve a sufficiently high pressure beyond of the inlet valve 80 so that it opens promptly and a large amount Air, preferably pre-compressed air or gas through the inlet of the open valve 80 in the piston head 40 flows into the cylinder.

Another novelty of the invention is that the piston 26 only A very short axial length of the fully cylindrical guide is still preserved.

It corresponds roughly to the piston head with the piston rings 3, radial Afterwards, only the piston fingers or piston arms extend from it 85 as guide parts to prevent the piston from tilting or tilting. The piston itself is now in order to achieve radial compact = gets so short that he no longer leads himself. The piston fingers or take the lead Piston arms 85 by being attached to the surfaces of the cylinder guide webs 23 slide. The pistons themselves now have a cavity between their arms or fingers 86. The pistons achieve an extremely small mass, so that they do many strokes per unit of time and, in addition, according to FIG. 8, both axial ends can of the central cylinder space 15 through lines 78 via outlet valves 79 into the Promote forwarding or summer lines 77.

The unit achieves the highest performance with low weight and Space.

Figure 10 shows that it is often expedient to use the fiction = to arrange the correct inlet valve inside the reciprocating piston. For example have the pistons 53 to 55 of FIG. 10 also include inlet valves, specifically the inlet valves 67. Otherwise, however, Figure 10 shows that it is possible today to use compressors for a high delivery quantity of gas or air of high pressure according to the invention rationally To create, the piston heads receive complementary shapes to the end faces the outlet = valves and the piston stroke is so far, or long, that the piston head = the cylinder top and exhaust valve end faces are pointed with almost no space in between touch. Furthermore, according to the invention, such valves are possible, that can withstand high temperatures and are cheap and quickly available in stores. For example balls as valves 63 or 64 of FIG. 10. These are commercially available for high temperatures and prints made of glass, porcelain, steel, carbon or hard metals available.

The complementary surfaces in the piston heads or in the inlet valve heads the inlet valves 67 are marked with "0" in FIG. 10. These ball valves do not require any special guidance Boundary spaces 90, 91, in which you can move around and open and close your seats are enough the end. This type of valve design is therefore particularly suitable for compressors with two-stage compression according to Figure 10 for the purpose of delivering larger Amounts of air or amounts of gas at high pressures. Here; it is shown in Figure 10 that the first piston 53 just has the lowest layer. The second first piston 54 has a higher and the third first piston 55 has an even higher one. This is to indicate that the three first pistons work one after the other. During the compression movement of the first piston in question 53,54,55 does the first piston compress gas or air and press it through the exhaust valve 63 out and with the achieved first high pressure in the second cylinder 56,57, or 58 into it, whereby this moves on the downward stroke of the pistons 59, 60, 61 moving therein fill with gas or air of the first high pressure. Then it moves relevant second piston in the second cylinder upwards to the already highly compressed To compress air or the already highly compressed gas even further and finally with the second high pressure via the second high pressure outlet valve 1 of the relevant Endzyl inders 56,57,58 through the collective delivery line 65 into the outlet or the Forwarding 66 to the combustion chamber assembly to forward. The first cylinder 50 feeds into the second cylinder 56. The first cylinder 51 feeds into the second cylinder 57 and the first cylinder 52 feeds into the two-cylinder 58.

The suspension of the cylinders mentioned takes place one after the other and the game then starts all over again, so that a continuous promotion of highly compressed air or gas with small fluctuations and fluctuations takes place. The fluctuations and fluctuations in the pressure and the delivery quantity are less, The higher the odd number of pistons and cylinders. Unsupported residual volume from dead space is only partial loss of efficiency because of the compressed air or Gas re-expands in it, thereby helping to drive the piston in question.

In the case of compressors of the design according to this figure, gas or Air pressures of 20 to 100 or even more bar can be achieved and mastered. Through this high efficiency levels of combustion engines with external combustion chambers can be achieved realize. The first piston and the associated second piston, so 53 to 55 and 59 to 61 measure to be positively connected to one another for their drive, z: m example by connecting rods and crankshafts so that they are in the correct timeframe together work.

FIG. 11 shows the longitudinal section through a similar venturi tube Nozzle through which I send a gas stream from chamber 72 towards chamber 76, while I feed fuel dust through line 74 to the nozzle. On what it Invention = what matters is that the speed of the pressurized gas to Example of the highly compressed air or the highly compressed water vapor in Input 72 in a certain ratio to the inflow speed of the fuel powder, For example, the coal damming exists through line 74 into the nozzle narrowing 73. In this way, the desired mixing ratio and the injection pressure are matched with the injection speed determined with the gas-powder mixture either through the nozzle 75 or through the water nozzle 76 into the combustion chamber of an outer combustion chamber or an inner combustion chamber an engine with external or internal combustion or a heating system should be directed. Whether steam or air is used depends on whether and how far the powder burns in the gas or air or not target. The gas, the air or the pressure = steam of the nozzle inlet 72 of the nozzle 71 may be taken from one of the compressors of the invention or in one the hot combustion chambers have been created as steam from water.

Through various details of the present invention and the invention (s) The patent application of July 13, 1982 made it possible to change the pressure range of the internal combustion engine with aeuseter combustion chamber arrangement so far in FIG First registration to move to the right, that the efficiency of the engine is the of the Otto engine or the Ptesel engine and the pressure is so high and the temperature in the combustion chamber becomes so high that both powder and liquid are in the combustion chamber or solid fuel can be burned.

At the same time, the power of the engine can be based on weight and space requirements It may be even smaller1 than conventional motors. Instead of, as in the Registration from July 13th to use water jets to atomize the solid fuel, According to the present invention, liquid fuels can also be used for this. This is especially recommended if the motor in question is under speed or underload Jaeuft. Because then it likes the temperature for direct combustion lack of solid fuel rods.

l) ie the main application cited in this patent application and those mentioned Pre-registrations, as well as the priorities used, are on the last Registration page still listed individually.

In one of the pre-registrations, under the term '' Voran = notifications if the main registration is included, it has already been described and shown how to use a shaft with lifting disks and a recess in between, a long piston stroke radially outwards for several pistons in several Zy = achieve relief at the same time and thereby the crankshaft with its high weight and can save space. But now there is a fear that very high speeds the inertial forces of the pistons can become so high that danger can arise; that the piston heads could be attached to the cylinder cover, because the pistons cannot be braked fast enough.

Figures 12 to 29 and 79 to 80 can therefore be left according to the invention so as to contain such a danger, or to prevent the unit for particularly high speeds j instes n = other as a pump or compressor, as well as to be designed as a motor.

Accordingly, it is shown in these figures that one is two in the same Axis diametrically opposite to cylinders connecting pistons with each other. Because it is thereby achieved according to the invention that the centrifugal force of one of the connected The piston of the other counteracts when the shaft 2 with the Hubschei = ben 4 stands still and the Zyiir erblock 3,33,133,233 etc. with the in its cylinders 13,14, etc. reciprocating piston 1,11, etc.

around the shaft 2 and the lifting disks 4, the centrifugal force of the one of the pistons counteracts the one diametrically opposite =, cancel completely the centrifugal forces do not, however, because one of the pistons of Jeweir Apart from a single moment per half cycle, the intervals are always different received from the center line 26,126, the shaft 2 and consequently the fleeing = forces periodically vary according to a sine function.

Because the centrifugal force does not only grow with the square of the angle = speed, but also inversely parallel to the distance from the axis of rotation. The relevant sine functions or cosine functions of the various types of offer can be found in the Fig'u - ren 64 to 66. But it is summary effective centrifugal force with the help of the connection of two pistons 1 and 11 to form one piston -pairs 1.11, by calling the pair piston from now on and its formerly Independent pistons 1 and 11 are now called piston heads, like the recalculation easily shows quite considerably less, which is a significant achievement of the invention is.

When the housing supporting the cylinder stands still and instead the shaft 2 rotates with its F-jut disks 4, the pistons have no centrifugal force, but then a cumulative acceleration force, this is so when connected Pistons of the invention more than twice as high as my earlier Finzel pistons 1 and 11.

But it is through the connection of pistons 1 and 11 and the insertion a piston shoe pair of piston shoes 5 in the arranged bearing beds 24 of the Piston and the guide of the piston shoes 5 with their inner surfaces 9 on the lifting surfaces or sliding surfaces of the piston-lifting disks 4 medium s of the present invention achieves that the piston 1.11 is forced to fire and no longer against the 7y = cylinder cap 333 can run because the contact between the sliding surfaces 8 of the lifting disks and the inner surfaces 9 of the piston string in question before 5 and the outer surfaces of the diametra in question opposite piston shoe 5 with the relevant swivel bed surface 24 of the piston 1.11 which is now prevented according to the invention. The connection of the piston heads 1,11 by means of the connecting webs 21,22 with each other, as well as the invention Arrangement of the column shoes, 5, the shaft 2, the lifting disks 4 and the swiveling bed surfaces 24 is therefore particularly suitable for particularly high speeds of the shaft 20 with a cam disk 4 executed stably. As a result, very high speeds, as desired, are possible.

In the figures are parts that are like parts of others of the figures replace, provided with the same final digits and only differentiated by the prefixes. The figures mentioned of this subject matter of the invention therefore all have the same Purpose, or complete the purpose, whereby they merely make different building possibilities possible = show things. The fact is that the parts mentioned are not straightforward can be assembled into each other, but one of the interacting Parts must be made in several parts so that the system can be assembled.

The construction of the invention part shown in the figures mentioned is therefore as follows in the figures mentioned that between two coaxial cylinders or chambers 3, 33, 13, 14, for example according to FIGS. 13 to 39 and 79, 80 or one or some of these gurcn, a centrally mounted shaft 2, 18, for example in lasers 12, rotatably mounted around a shaft axis 26 perpendicular to the common axis 25 of said chambers 13, 14, perpendicular to and through said common axis is and axially a central recess 16 by the distance "e" = 6 away from the shaft axis with the radius "R" 7 formed Hubsche wen 4 with about the Cxzenterachse 23 cylindrical guide surfaces 8 of the radius "R" around the said eccentric axis are, which are the inner fluechons 9 of two in the piston 1,11 in its at a distance 19 with a radius 100 formed swivel bed surfaces 24 with the piston shoe outer surfaces 10, also from the genan ntem radius 100, pivotably inserted piston shoes 5,55 touch and / or guide, whereby said piston 5,55 extends into both of the chambers 13,14, as well as being axially reciprocating in them sealingly along said common axis 25 , and said piston in its axial center forms a cavity 27 through which a part of said shaft 2, 18 extends and which is delimited by at least two connecting webs 21, 22 which connect the two piston heads 1 and 11 to one another and thereby both Piston heads 1 and 11 are held together in a non-positive manner; that the mentioned lifting disks 4 in places di? Outside = surfaces 28 of said piston 1, 11 protrude, said connecting webs 11, 22 enter said recess 16 and are arranged between said two said cam disks 4; doss the named outer surfaces 28 of the piston 1,11 on the inner surfaces 29 of the chamber housing 3,33 in a sealing manner or slide and thereby close the named chambers 13,14, as well as during their axial movement along the common axis 25, i.e. at the mentioned reciprocation, enlarging and reducing in the relative inverse ratio; that said axial movement of the piston 1,11 is generated or guided either by fluid pressure in said chambers 13, 14 or by the movement (rotation) of said cam disks 4 or by both; that the cited lifting disks 4 are provided with cylindrical axial extensions 18 around the cited shaft axis? 6 and with these are fastened to the shaft 2, the cited extensions 18 also at the same time the cited bearings 1? can carry or are stored in them; that at least one of the chamber housings 3, 33 is provided with a removable and attachable cover 333 in order to enable the introduction of the said piston 1, 11 into the relevant commons 13, 14 that the piston 1,11 between its two axial ends 24 has a length that is only slightly shorter than the distance between the chamber base 30 reduced by the stroke of the piston and the bulge is arranged according to claim 13 that despite the mentioned only small distance the piston ends 24 can never abut the chamber bottom 30, since the support of the piston shoe surfaces 9 and 10 on the swing bed surface 24, or on the guide surface 8 prevent this; that several chamber sets 13, 14, in chamber housings 3, 33, 133, 233, for example according to FIGS one of said pistons is provided with at least 4 connecting webs 221, 321, 222, 322, for example according to FIGS. 20 to 24, and said at least four connecting webs are arranged to the side of the two interposed connecting webs 121, 122 of another of said pistons 1,11; that, for the example according to FIGS. j to 27, a pin 34 which attaches connecting webs 121, 122 to the piston heads 1, 11 of said piston, is arranged, engaging in a recess 31 of a piston shoe 5; that, for example, according to FIGS. 28, 29 or 30 to 32, several pairs of lifting disks 4,444,104,204 are arranged rotated at the same angles on a common shaft 2 in the direction of the distances "e" of the eccentric axes 23; that, for example, according to FIGS. 33 to 37, a pressure line 45 is arranged through a chamber housing 3 and the piston 1, 11 has at least one groove 48 for connection to the mouth of the.

relevant pressure line 45 is provided and, if necessary, also contains bores or channels 47,49, which conduct fluid from said line 45 into pressure fluid pockets 38,39 of a piston or piston shoe 5; that the piston heads are provided with recesses 50, 52, for example according to FIGS and the piston head 1,11 engages around and fastened or fastened to it that in said piston 1, 11, in the respective piston head 1, 11, for example according to FIG 56 by compression springs 58 inside the piston heads 1.11 are pressed inward, so towards each other, for example to compensate for the changing distance "A" of Figure 80 during rotation of the shaft 2 and the cam disks 4 and / or, whereby the pressure of the above-mentioned springs 58 is held stronger than the inertia forces that may occur on the pistons 1, 11 Which of these arrangements and configurations are used in practice largely depends on the desired speed of the cylinder block or the shaft 2 with the (the) Lift disks) 4.

If the speeds are only low, the arrangement can be used of the piston of the figure group 12 to 29 and 79 to 80 renounce at all and use the simpler and cheaper solution after pre-registration. Before you that decides, but should be based on the kinematic-mathematical conditions calculate exactly.

FIGS. 40 and 41 show the general structure of an engine of the invention in an exemplary manner. Relaxers of the conventional ones are shown here Engine design with crankshafts and connecting rods. The crankshaft acts as the compressor in these figures a double compressor for two stages, low pressure and high pressure drawn in according to FIGS. 12 to 29, specifically each of these compressors four or six pistons with a corresponding number of cylinders. The compressor 2 with pressure in the compressor 3, which then the high pressure in the combustion chamber 5 supplies.

The arrangements in the combustion chamber are special, with these exceptions in FIGS. 40 and 41 still for example or as an alternative, in the part figures 53 to 57 are shown and the technical assumptions about the thermal conditions are explained in FIGS. These contain preliminary information that in the coming = the practice will probably still be made more precise or corrected will.

First of all, the inventor looks at the engine without using it of solid or powdered fuels, in the sense of the main application as gasoline or diesel fuel engine. That you have such engines with an outer combustion chamber between a compressor or compressor sets and an expander or expander-Sat e can build has been known for a long time, but such engines have hardly been bouted. The inventor suspects that this is due in particular to the technical means were not sufficiently well known for this up to now. Because the engine builders are concerned essentially deals with the knocking phenomena, the combustion chamber formation and that the combustion chamber design with a relatively large volume and a relatively small inlet or outlet Compressor pressure, i.e. with a small compression ratio eta.

One refers to the PV diagram of the Otto, Diesel or the engine of the mixed process and sees from this that at a given pressure below the self-ignition temperature of the fuel-air mixture the smooth-space internal combustion engine is visibly economically superior to the constant-pressure internal-combustion engine. Gas turbines are used in aircraft construction, but a European gas turbine with shaft output costs three times more than a three times more powerful American shaft gas turbine. The price of the European turbine under consideration is ten times too high to be used in people's planes and bought by people with average incomes. There is therefore a need for cheap, powerful aggregates that are not currently on the market.

There is still a lack of companies to mass-approve the shaft-type gas turbines Build prices, if you disregard the power-wise to large USA turbines. The inventor's efforts in recent years have looked to no hope let the desired shaft gas turbines be available soon, although the turbo-charger technology is so advanced that such turbines should actually be cheap on the market.

Therefore, the inventor has studied the problem and is to the impression come that the engine with an outer combustion chamber between a compressor and Relaxation sets then noticeably higher performance per weight, dimension and A price higher than the well-known Otto and diesel engines, if one succeeds to make such an engine with an external combustion chamber technically more perfect. This solution the problem described appears to the inventor with the help of his technology and the Patent application group is quite possible.

Because what is important in order to make such an engine efficient is to bring the pressure in the combustion chamber high in order to obtain a favorable efficiency in the PV diagram, which is based on the formula can be calculated.

In order to achieve the high combustion chamber pressure, it essentially comes down to it on building the compressor without dead space or dream-free, the expansion valve To build with little dead space and to create valves that make this dead space a reality help and also the increased temperature load during the transition from Withstand the combustion chamber in the vent. Then it will be so that the relaxer He does a full job with every single downward movement, while he does that with Otto The engine only works every second downward movement.

The engine with an external combustion chamber is therefore suitable for the same Decelerator almost twice as much work to do as the Otto engine.

So it is noticeably lighter in weight than the Otto engine same performance. Because the weight of the required compressor is relative low, as this is due to the lower temperatures in the Essential can be built from light metal and also only about a quarter to a third of the stroke volume of the expander is required. The invention is therefore concerned with considerable Share with the creation of lightweight, almost dead-free compressors, for example those of Figures 7,8,58,59 and with the procurement of better coolable valves between Combustion chamber and expansion valve, as well as with the shape of the cylinder head inner surfaces and the end faces of the piston heads to avoid dead space or dead space poverty to be realized. In addition, there is the arrangement of wide, thin flames in the combustion chamber, to ensure good combustion of all incoming substances and this distribution of the fuel and the air not to the supply in a big cylinder, like in conventional engines, to be left. This perfection of combustion by the invention will thus still contribute to the gasoline or diesel fuel To make the engines of the creation more efficient and more efficient, where the more complete combustion may also be useful for exhaust gas detoxification.

With these achievements for the Benir or Dicseltrs, ibstoff Engine with outer combustion chamber through the invention you then have the basis for it reached to think about the combustion of solid fuels, which promise Burns even better than the previous coal dust. They are more compact so they require less space per weight than pulverized coal and they are more pleasant in handling. Here again the introduction of the thin, broad burning flame Significant through the invention, because they no longer use the fuel supplied left to chance of correct mixing with the air.

Because it is according to the invention, in particular through the figures 7,8,58,59 is possible, one-stage high pressures efficiently in the combustion chamber entrance To promote, the engine is also more rational than the conventional steam engine with all the refinements, so that the engine to 2/3 to 3/4 of the imported oil devouring electricity generation and central heating can be used, The engine apparently allows for smaller systems than today's district heating plants and electricity works, so that it is also bought by relatively small communities and used for heating and electricity supply with generator operation, the Generate electricity and heat cheaper than the previous oil-powered power plants or the steam engines power generation = plants.

The operation of the motors of Figures 40 and 41 is essentially so that the crankshaft 1 is started by a ueb @ chem starter motor. Included the crankshaft 1 rotates the compressor 6 iXr the compressors 2 and 3. It is For example, in the combustion chamber 5, the lock 6 is closed, so that the first compressor 2 under medium pressure via intermediate chamber 4 in the high pressure compressor 3 ge = delivered and delivered by the second compressor 3 under high pressure into the combustion chamber inlet 200 hot compressed air with a temperature above the self-igniting temperature of the fuel high compression temperature cannot escape from the combustion chamber and become in disem jams in front of barrier 6. Since the fuel drive rollers are simultaneously with the rotation of the crankshaft 8 already feed the fuel 28,45 into the burning point between 27 and 37, ignites the fuel and burns in the compressed air, with a sudden, higher under constant space combustion, as occurs in Otto engines, this pressure can you use to use a push button 51 behind line 50 to use the To move the flap piston 666 upwards so that it opens the lock 6 and afterwards The opening is locked in the open position of the lock 6. This is just one example of the ignition. Once the ignition has taken place, the gas flows through the combustion chamber 5 over the possibly arranged cleaning songs system 40,41,42,43, 44,57,58 etc. and over prepare the valve 12 through inlet openings 10 in the relevant downward stroke Cylinders 13 to 15 periodically alternate one after the other to include the relevant To drive piston 16 to 18 periodically one after the other to the work-Downshaft, the then in turn drives the crankshaft I so that the compressor set drives and the Outputs work to the outside of the crankshaft, which is still the valve or the valves 12, e.g. via 31 to 33 may drive. The engine is running now with constant combustion chamber pressure until it is switched off. being its performance may be regulated by regulating the speed of the fuel drive rollers 8.

For example connected to the accelerator of the car. While here the compressor of the group of figures 12 to 29 is drawn in; it seems so be that the compressor of figure group 7,8 and 58,59 together with those one of the pre-registrations the compressor work even better and in one stage can perform, so that this the arrangement of the compressor of Figures 40 and 41 like to replace. They can run on the middle 15 at the same time = the piston 26 of the mentioned figures from the outside at the same time parallel the mentioned pistons 26 drive by means of lifting disks or crankshafts and connecting rods, so that the 3,4,5,7,6,8 or 9 compress pistons 26 simultaneously and parallel to one another to the center 15.

Some of the details of the desired valves are already described in the previous registrations, including the principle of combustion of the solid fuel in the combustion chamber 5. This patent application therefore shows further details of the possible design of compressors, expanders, valves and combustion chamber alternatives that Realize the desired goals in detail by the fact that the fuel is initially pulverfoermit or powder is mixed with liquid, for example with some water, and is fed under pressure to a nozzle that is so narrow in cross-section that the powder closes under the pressure a narrow powder compacted, in particular into a flat cross-section with a width greater than the thickness of the cross-section and the powder is pressed out of the nozzle in the form of a thin strip; or; that the cross-section of the fuel rod is wider than it is thick and enters a nozzle filled with hot air, the cross-section of which is thinner than it is wide; or; that the fuel belt, along with other fuel belts, is guided through corresponding cross-sections, so that as a whole there is a wide, thin feed of the fuel into the combustion chamber; that the said combustion chamber is that of an internal combustion engine with external combustion, into which a compressor blows hot, compressed air and the combustion chamber is followed by an expander, into which the combustion chamber delivers its hot gases and the said expander drives the compressor and above Excessive relaxation work is poured out to the outside, for example in FIGS. 40 or 41, in which the compressor (s) 2, 3 is connected to the inlet 200 of the combustion chamber 5 and the outlet 10 of the combustion chamber to the exposure chambers, e.g. 13, 14, 15 periodically one after the other is connected, so that the working elements, for example pistons 16, 17, 8 one after the other with hot gas from the combustion chamber 5, for example via a control or valve arrangement 12 with inlet means 10 and outlet means 11, are periodically charged to their working and expansion stroke execute and, for example, drive the compressor elements 19 to 24 via connecting rods and a crankshaft and In addition, work through the crankshaft out of the housing 30 to the outside; or; that a valve 12 is arranged, with which all entrances to all expansion chambers, e.g. 13 to 15, are closed, so that when the engine or its crankshaft 1 is started by the compressor e.g. 2, 3, highly compressed hot air is accumulated in the combustion chamber 5 which is blocked from being able to escape into the expander, the air pressure rising and the temperature so high that the fuel ignites and burns in it; or; that after the fuel has been ignited, a passage to the expander is opened or automatically opened, for example by means of a pressure or temperature sensing means, e.g. 7; Or; that between the ignition chamber part 27 of the combustion chamber 5 and after the ignition pressure of the above-mentioned lock 6 has been exceeded by a feeler piston 51 loaded by a spring 54 and the pressure is then passed under a lifting element 666 quickly and in accordance with the delivery pressure from the compressor and the gas intake by the expander (13-IS) or is opened by a system causing the analogous effect, for example according to FIG. 41; that the fuel is stored in a chamber 44, d de @ a non-combustible gas a pressure is fed through a line 144: is. that corresponds to that of the combustion chamber 5 or that of the compressor run; that the fuel 45 is a band-wide thin cross-section and a conveyor set, for example a pair of rollers 8, is arranged so that the fuel under seal as a tape or band 45 is introduced into the nozzle 27 in the speed that for burning with the desired air @ erhae @ tnis "lambda" in the hot air in the said nozzle27 is required; that the burning point 27 is assigned a nozzle-thick adjusting element or nozzle cross-section adjusting element 46, for example according to FIG the air pressure that comes out of the compressor can be influenced in order to optimize the fuel, ffes 28,45 in the combustion point 27 or in the combustion =.

chamber 5 to effected; that in front of the intspanner, for example 12, 13 to 15, a dirt or foreign matter separating system, for example 42-44,55,59,60 with rotor drive 41 is assigned, which may be arranged interchangeably and / or by means of the holder 40 the facility can be added to or removed from it, if so desired; that it contains a crankshaft 1 which, by means of gear means, drives the valves, for example the rotor valve 12 and the compressor part, e.g. 3, 4, 19 to 24 and / or the compressor part supplies a higher air pressure in front of the combustion point 27 than it does in the combustion chamber Main part 5 is present, so that the hot air is pressed through the nozzle 27 under excess pressure and a special thickened and hot air is present where the fuel tip enters the air, or the fuel dust is pressed into it; that, for example, as shown in FIG. 54, fuel mixed with powder or powder and water is pressed from a line 68 with compression in a tube 69 of narrower cross-section into the combustion point 72; that the fuel rod or the fuel belt 28 is forced into a narrow nozzle 64 without first passing through the combustion chamber 5, in which the hot compressed air coming from the compressor is introduced from the inlet 63 of larger cross-section into the narrower cross-section of the nozzle 64; that for example air inlets 64, fuel inlets 69, nozzle lugs 70 and 71 formed according to Figures 54 and 55 are arranged and a nozzle cross-section adjusting means 65 by means of a guide surface 66 the nozzle cross-section at nose 71, with cross-section 73 or with nose 70 or several these points are expanded or narrowed as desired or according to automatic control, in particular a thin, wide cross-section 73 according to FIG. 55 is expanded or narrowed in order to produce a thin, wide combustion chamber with highly perfect combustion; that between the separating space 5 or 65, the air inlet 67 and the fuel supply duct 76, for example according to FIG. 56, the nozzles 71, 181, 281 with the ignition point 85 are arranged and these lugs can be brought closer to or removed from one another, for example by means of eccentric pressed parts 78 , 79 and 82, 83 in rooms 77 and 84 Beyond the thin walls 80, 81 which yield under eccentric action and which support or form the aforementioned noses 181 and 281; that the combustion chamber 5 is lengthened by means of a channel 65 to behind the engine and there a removable part 88 is arranged below it, which contains the dirt odor foreign body collecting system 89, from the bottom of which a forwarding channel 90 to an intermediate channel 91 in the combustion head leads, from where the hot working gas is then located through the combustion chamber outlet 92 to the relaxers, the removable part 88 sitting on a holding surface of the burner body and, for example, held on it by means of a bracket 93, or by means of clamps while the vehicle is being driven 94, 95 and guide plate or holding plate 93 can be pushed out and replaced by a new one when the debris collection system has become full, as described, for example, in FIG. 57; that it uses compression systems that have low dead space and a high degree of conveyance at high pressures, for example systems according to one of the previous registrations or according to this patent application, so that even at pressures above 20 bar to above 100 bar they still promote highly efficient compressed air to one ensure high engine efficiency; that a water injection system 86 according to Figure 56 or one according to Figures 72 to 76 is assigned to an engine with an external combustion chamber or a gasoline or diesel engine using the teachings or mathematics of this patent application.

The figures 4? to 44 show the example of a valve that one Compressor upstream or downstream, or also ZUrTl L3eispiol the tensioner of the motor of lines 40 and 41 or any other motor or expander can be assigned. Figure 44 shows this valve in longitudinal section, while Figures 42 and 43 are cross-sections through the valve as these Figures Longitudinal sections are through a cylinder, the 7-cylinder head containing the valve 12 or valve head 27 ct.

Both Figures 42 and 43 are the same sections. They only show mutually different stroke heights of the piston 4 in the cylinder 1 and caused thereby other positions of the ritable valve 12.

In this valve, what is known per se should be achieved once rotatable valves can really be used reliably in practice and moreover should be achieved that a valve between combustion chamber 5 and the expansion valve can be used that can be cooled much better than the previous ones Lift valves.

If possible, it should also have a self-sealing feature = Realize the effect and if necessary, if it should wear out, yourself again run in tightly or lap in tightly. It should be noted that the gas temperature, which this valve touches and flows through = higher than in conventional gasoline engines is. Its meaning is that the rotating valve body 12 is hollow and is forcibly flowed through by cooling fluid, for which purpose the valve opens the internal cooling spaces 13 and 29 respectively. In addition, it is by pressure piston 16 against the Sealing bed surface 32 pressed in the cylinder head bed so that it always works tightly. The pressure takes place in the opposite direction to the inlet channel 10 and the cylinder = inlet 106. Hence the inclined position of the pressure piston 16 in their Andrueckkammern 15. In addition, a sealing block set 20 is to close the Inlet channel 10 (later in the rotation 11) arranged, which the inlet channel 10 or 11 closes when the valve with channel 10 or 11 over the Inlet port 8 of cylinder head 27 rotates out. Also this set of sealing blocks is pressed against the outer surface by pressure pistons in pressure cylinders (21 in 22) 6 of the valve 12, respectively. pressed against the support surface 24 in the head 27.

The pressure piston 16 and the sealing blocks 20 are pairs that are axially viewed relative to the valve axis 112 to the side of the inlet or outlet channels 10, 11 and the cylinder inlet 106 are offset, so that the inner sliding surfaces the piston 16 and the Kloetze 20 always closed on all around, uninterrupted Outer surfaces = parts of the valve body 12 run. The feeding of the pressure chambers 15.20, for example, through channels 18.23 from the combustion chamber or instead To conduct gas from the combustion chamber into these chambers, a separating valve is added one of the pre-registrations in order to supply the pressure on the pressure chambers 15,22 To let lubricating oil work, so that the chambers 15,22 then always lubricating oil from Pressure equal to that of the combustion chamber pressure included.

Furthermore, because of the arrangements 34 to 36, the valve may also be eccentric and counter-springing at the other end, 37,38,39 periodically moved axially back and forth so that a rotary movement and an axial movement are superimposed the sliding and sealing surfaces 6,7,31,32,120,17, etc. of the valve, the valve bed and the pressure piston, as well as the sealing block, try to ideally lap in.

Here, too, it is of particular importance that the shape of the piston heads, So the end faces of the pistons 4 in the cylinders 2.1 have a shape that of the the inner surface parts of the system above the cylinder are complementary. One sees therefore, in the figures, the front part surface 5, which corresponds to the radius of the outer surface, is clearly visible 6,7,31 of the valve 12 is complementary, as well as the sloping surfaces that share the sloping surfaces of the passage 106 are complementary and the flat end faces continue to be outwardly = parts of the piston 4, which complement the planar surface parts of the cylinder head base are. So there is no dead space here when the piston is fully on the surfaces of the upper parts is brought up.

It is also important here that it is also shown in FIGS. 42, 43 is that the exhaust gases are at the lowest position (outer dead center) of the pistons 4 through Schlit = ze 3 arranged in the lower part of the cylinder in a collecting chamber for Exhaust can derive. This is advantageous because it eliminates any leftovers of foreign substances escape more safely than with the return through a Valve, because the fewer sliding / telling foreign matter or fuel residues pass through, The lower the risk of piston or cylinder wall wear in the expansion valve.

So the details of the engine of the invention promise long Service life of the pistons and cylinder ends compared to conventional coal dust engines to have. As far as the temperatures when passing through the valve prove to be too turn out to be high, according to the calculation of the invention, water is injected in order to to cool the temperature.

As shown in FIGS. 60 to 63, the mean water temperature can Cylinder gas temperature to below 300 degrees Celsius, but with a loss of efficiency be reduced. Consider here on the basis of the diagrams in FIGS. 60 to 63 that the combustion chamber temperature in the expansion cylinder is only effective for a short time. The most sensitive So part against temperature is not the expansion piston or cylinder, but the flow control valve according to the previous notification or that according to FIGS. 42 to 44.

The details or alternatives for the design of the valve 12 and its surroundings and aids for achieving the desired goal of good tightness and control of the gas flows is achieved, for example, by having a chamber through which fluid flows, for example chamber 1 according to FIGS. 42 to 44 which, for example, need not only be chambers of a hydraulic pump or a hydraulic motor, but also chambers or cylinders of a compressor, compressor, gas engine or expander or an internal combustion engine, such as cylinders 1, e 2, 3, 13 to 15 of the Compressor or expander of FIGS. 40, 41, a circulation valve 12, which is mounted in a bed 32 and rotatable with its outer surface 31 in said bed, is arranged upstream or downstream or upstream and downstream, which has a cylindrical outer surface 31 as a sealing surface Has seal on the Bettflaeche 32 and which has a radius that corresponds to the radius of the adjacent Kol benkopfes, where the chamber 1 preferably contains a piston 4, the head of which is secured against rotation, complementary to the said outer = surface 31 ^, tirnfloocho 5 mtE radius, the said valve contains inlet ducts 10 and outlet ducts 11, and characterized in that the valve is pressed with part of the outer surface 31 against the bed surface 32 for the purpose of a good seal; that said valve 12 has inner cavities 13 or 29 through which cooling fluid such as air or water may flow, and / or that said valve is by means of an axial drive, e.g. 11, 33, 34, 3 ': t , 36,37,38,39 periodically moved axially, i.e. oscillated or reciprocated, so that the rotary movement is overlapped with an axial movement for the purpose of self-cleaning of the sealing surfaces 31, 32 or for the purpose of self-sealing of the said sealing surfaces 31, 32, and / or , wherein a channel 13 is arranged with openings 14 for the purpose of purging the named chamber with cooling air, and / or, wherein in the named chamber is a cylinder in which a piston 4 runs, which in its lowest position slits 3 in the chamber wall 2 releases so that the exhaust gases escape from the rammer through these slots, and / or, in which the exhaust gases are passed through the outlet channel 11 and 9, and / or, in which the channel 9 in the chamber head 27 cooperates with the channel II in the Vent il 12 occasionally flushes chamber 1 with cooling gas or cooling air under pressure or running air or drives the exhaust gases out of chamber 1 through duct element 3, and / or that valve 12 is diametrically opposite inlet duct 8 in valve head 27 and inlet 106 into the Chamber 1 is assigned a pressing arrangement, which consists of two or more pressing pistons 16 in Rnpresszylindern 15, whose pressing = pressure is directed to said channel 8 and inlet 106 and which are axially offset parallel to axis 112 of valve 12, so that one of the pressing pistons this side and the other beyond the channel 8 and 9, as well as the chamber inlet 106 and thereby touch an uninterrupted part of the outer surface 31 of the valve 12, and / or that pressurized fluid, for example. is passed through channels 18 into the pressure chambers 15, this lubricating fluid can be that via arrangements one of the advance notice with the gas pressure in the duct 8 and the inlet 106, but can be separated from this gas with the arrangement of the advance notice , and / or that the chambers 15 and piston 16 are dimensioned and directed in such a way that the outer surface can slide with a rotation and / or axial movement of the valve 12 without high friction on the bed surface 32 and against it seals well so that no gas or fluid can escape from the chambers or spaces assigned to them, or that escaping fluid is a minimum, and / or that in the Veflti Ikopf 27 an inclined surface 24 of a chamber 19 is arranged on which a sealing block 20 rests with its bearing surface 25, and / or that said sealing block has a sealing surface 120 which is shaped complementary to the outer surface 31 of the valve 12, olso a partial cylinder surface e 120 forms with the radius that the outer surface 31 d <es valve 12 has, and / or, in the valve housing associated with the relevant sealing block, a pressure piston 21 in a pressure = chamber 22, which may be filled with pressure fluid through line 23 , is arranged, which presses on the pressure block 20 and presses it with the surface 25 on the surface 24 and with its sealing surface 120 on the corresponding part of the outer surface 31 of the valve 12, so that the said sealing surface of the block 20 presses the relevant passage 10 rotating past or 11 of the valve 12 closes and seals when it is in communication with the channel 8, and / or in which such a number of sealing blocks 20 with associated pistons 21 and chambers 22 are arranged as pistons 16 are associated with valve 12 , and, or that the blocks 16 have the same axial position relative to the valve axis 112 as the aforementioned pressure pistons 16.

FIGS. 45 to 52 and partially FIGS. 64 to 71 show Examples of motors of the invention for highest, at least short-term performance with great simplicity and cheapness and with low weight. Your job is it, for example, to replace the shaft gas turbines for short-term use and at the same time almost or completely the same performance per weight, depending on the situation = leadership type, Or it is your task to control the performance = output of the relevant engine directly in Druckfluidstroeme, for example in Hydrotluidstroeme to convert.

The conversion of an internal combustion engine's power into one or more Pressurized hydrostatic fluid flow is known from U.S. Patents 3,260,213 and 3,269,321 and other patents of the inventor known in other countries. Back then were these patents, however, are not taken seriously by the technical experts. They were held to Example contrary to the fact that the transmission of a hydraulic power in pipes more losses bring than you gain in advantages.

In addition, the patents at the time had a sound theory = reason, but the mathematical and technical "know-how" and knowledge was not reached in order to be able to use the engines in practice or to be able to enforce them. The corresponding Figures of the present invention are supposed to address these shortcomings of the old technology overcome and power-concentrated aggregates of low manufacturing costs and to create weights. In addition, the output should, as far as possible, in the middle between the cylinders so that the cylinders are on both sides can protrude from narrow aircraft parts into the air stream, or it a single crankshaft assembly is supposed to be an aggregate with working lifts in both Axial directions of movement are assigned. Because so far the crankshafts have been working Yes, only in the case of an axial movement of the piston with work output to the outside. In the end Means should be arranged to spoil several such free-flight piston engines, To force the same work cycles so that the performance of several of the same = rationally can be transferred to hydrofluidic units with at least seven pistons. and Finally, the weights of such free-flying pistons should be reduced noticeably and the frequency of the number of strokes per unit of time should be increased, which is possible as a result is that the free piston according to the invention compulsory means to limit movement assigns that a approaching the piston to a cylinder cover on the other side impossible if the piston flies too quickly. Because that is a prerequisite to increase the stroke frequency.

According to the invention is therefore in Figure 45 between two pistons 2.4 arranged a central wall, into which a feed is carried out by turbo and a return Lagventil is arranged that makes outflow of pressurized gas impossible if the control groove 5 or 6 flies over the inlet 25. Also is fuel injection provided instead of a carburettor to enable a long piston stroke. This aggregate therefore gives the utmost compactness and cheapness of manufacture with extraordinary high performance. The power may be taken off at one end 7 of the shaft 3 of the piston will. The engine works in both directions, one of the cylinders in one the axial lift directions.

Figures 46 to 49 show measures, the hydraulic pumps between to arrange the cylinders so that the cylinders are on the outside and in the air flow protrude from both sides of a narrow part of the aircraft. In addition, in This figure swivel = arms 32 arranged so that the hydraulic pump piston no high Relative = suffer speeds or tilts under high pressure.

Figure 50 with its formulas in is of particular importance Reference to the templates or hydraulic pumps drive elements 43, 44. Because through this previously unknown formulas it becomes possible to control the work output of the internal combustion engine 1 ben 2.4 exactly dimensioned fully to the hydrostatic pressure flows from the pumps = Piston 39 to be delivered. The engine then works with no power residue and no power or fuel waste, which has never been achieved before. One can at the Template 43 then arbitrarily near the end of the stroke a power demand reinforcement cling or shaping so that it weighs the internal combustion engine piston stroke and thereby the approach of the free-flight piston 2,3,4 against a corresponding part, For example a cylinder cover, or walls 15, 115 or 215.

Figures 51, 52 combine a forced limitation of the piston stroke the piston 2,4 by means of the arrangement and the engagement of one of the lifting disks of the Invention in the middle part of the piston skirt.

At the same time this version shows the possibility of the arrangement tion of many hydraulic pistons and the guide of the lifting part 62 against Twist or displacement. Instead of one of the lifting discs of the invention in the middle To arrange between en engine pistons 2.4, you can also use a crank shaft and connecting rod in the middle between engine pistons 2 and 4. But it's not that easy and not possible without side loads, since the crankshaft has not yet been used could easily pass through the piston or the piston skirt. In the present In the case of the invention, however, this is not shown in the figure, then possible if you move the crankshaft or the piston shaft 3 for the purpose of installing a Piece of the crankshaft in the inventive groove 47 of the central piston rod 3 built in between pistons 2 and 4.

So far, the arrangement of the lifting disks of the invention is opposite the arrangement of a crankshaft drive or guide means the much simpler one. However, if possible, as is not shown in Figures 51 and 52, the arrangement according to FIGS. 79 and 80 can be assigned to the lifting disks. Example = wisely, by taking the reciprocating piston 56 with the compression springs of Figure 79 into account the distance calculation according to Figure 80 on the middle part! of the piston skirt 3, for example on or in the parts 49 of FIGS. 51, 52 so that the Ro I lenbolzen 50 of these figures within the central part 49 within the limits the dimensions of Figure 80 strongly against the Fuehrungsflaechen 8 of the lifting disks 4 can be pressed with such a strong pressure that this is possible the approach of the free-flight pistons 2.4 to cylinder covers or boundary walls on the other side turns off or prevents.

FIG. 64 shows a section through a conventional four-pack Otto engine. For the purpose of comparing the performance of the systems, all figures are 64 to 71 drawn to the same scale, namely in the one drawn in under FIG. 69 Scale 1: 3., So reduced three times. The figure 64 is based on many measurements the Honda 750 cc motorcycle engine CB 750 of the sixties and seventies. These umout has proven itself very well in the test stands of the inventor. One has at the 60 mm diameter piston and 60 mm piston = stroke including ignition, etc. a weight of 12 kg; namely about 5 kg each for the crankcase with piston and crankshaft and connecting rods, as well as 5 kg for the cylinder block with valve head are two kg Equipment, such as ignition, hoods and so on, thrown down by the four fi-cylinders of this engine on one. Without the Trurbocharger, the output is 18 P'S at 10,000 Uprn. Indeed the machine only runs 8500 without turbo. Achieved with a turbo built by the inventor this engine at 10,000 rpm per cylinder is equivalent to 26 hp at 14 psi boost pressure, The engine can easily withstand 10,000 rpm if strong bolts are used are. You can increase the boost pressure to double that and thus the performance Increase it still further, but then it needs good cooling. In short-term motorcycle races in the USA the services are used around twice as much, for example with Methanol as fuel and very high turbo boost pressure.

The performance data in the figures mentioned are therefore not exhaustive taken out of the air and by no means the highest possible. Everybody should have the high ones Services are only used for a short time, for example half a minute on a vertical ascent of a trough wing plane, so that the motors do not get thermally out of balance, so that the motors do not heat up too much.

Taking these cylinder outputs into account, the result is values entered to the right of the figures. Figure 65 is the Burke Engine of the late American Burke with Scotch-Joke as. Piston guide, however improved by the present invention that the Scotch Joke, as Burke sewed it, so the part 8,6,7, according to the invention with the outer surface 11 on the inner surface 10 of the middle part of the housing so that you can do without the pre-compression cylinders and replace them with turbo chargers can. This is how you get the high performance per weight of this unit.

The four-cylinder aggregate of the present invention would have to go Even a much higher performance result if the piston stroke limits and forced guides the invention should prove itself in practice for a sufficiently long time. To consider is that the engines on the page with Figures 64 to 66 relate to four-stroke engines. The performance of the two-stroke engines on the focus sides with Figures 67 to 71 are correspondingly higher because they have twice the number of power output lifts. The figure 68 corresponds essentially to the figure 45, but to the comparison size redrawn. With turbo drive it brings an incredible performance, the dos power-to-weight ratio of the shaft gas turbine mentioned. Allerdinqs isn't one yet Power transmission the power output provided. The exhaust gas from the relevant cylinder outlet 29 promotes the turbo-charged air via the inlet valve via turbo or charger of the invention and the control grooves 5, 6, into the relevant cylinder 27, 29.

In Figure 67, on the other hand, no turbo charging is provided, but rather are light pre-pressure cylinder 100,200 arranged with pre-pressure piston 202,203, the pre-stressed Charge air flows from channels 205,206 via the inlet 19,119 with the invention Valve 19,119 in the relevant cylinder 27 or 29 in. The performance per weight is therefore a little less than that of Figure 68, since the turbo is a little less than the light pre-cylinder orders are 200,100.

The performance of the machine of Figure 69 of the invention is somewhat lower power-to-weight ratio, which is due to the fact that this is already a mechanical one Power output by means of the lifting disks and piston guides according to the invention are built in. Nevertheless, the power-to-weight ratio of almost 7 hp per kg is very high, when the unit of the invention can hold out reliably and reliably at 10,000 rpm with turbocharging should.

The high performance of the unit of Figure 68 brings first of all next not yet a high sense, because there is no gear mechanism to reverse the Achsiol movement is arranged in power output to the outside.

In addition, synchronous running in time one after the other is often more phisisEt rer aggregates desired. Therefore, in Figure 70 at the axially outer end of a the piston, for example on piston 4, a crankshaft drive with connecting rods and crankshaft arranged. This arrangement reliably prevents the piston from flying up a one-cylinder end or on the middle wall 15. And besides, it is opposite conventional ones engines because it saves the second crankshaft and connecting rods that would otherwise be needed are required for two cylinders. The power-to-weight ratio, two-pack and turbo-charged, As in FIG. 68, this is extraordinary despite the arrangement of the crank mechanism high.

In Figure 71 there is a triple set of this unit with forced synchronization the lifting of three units by common crankshaft 126 is shown. In the performance evaluation once with and once without the eight pumps 130 to 137 in the crankcase for the Conversion of engine power into hydrostatic pressure currents.

The targets of the aggregates of Figures 45 to 52 and 64 to 69 become For example, the aim is that the investment in the substance is a double Free flight piston engine, for example according to Figures 45 to 52 or 67, 68, 70, 71 is, in which in two chambers 27 and 29, which are separated by a central wall 15 from each other are separated, two pistons 2.4, the rod 3 firmly together by a Kol are connected, which penetrates the central wall 15 sealingly, oscillate, that is, reciprocate or run back and forth in the axial direction if the relevant chamber is through Inlets 25,16,17 are supplied with fuel and in the compressed air in the relevant Chamber is ignited, and in which control cross-sections axially fixed relative to or on the piston, for example as grooves 6 and 6 in the piston rod 3 are through which the relevant chambers through the at least one central wall 15 filled with air or a mixture of fuel and air and outlet channels 29 exist that make up the gases that do their work on the piston in question 2 or 3 have given in the relaxation in the relevant chamber, escape can; or; that an inlet 18, 25 is arranged in said central wall, in which a check valve 19 lets gas into the ring comer 18, but none through the valve 19 out or back, as well as that the botroflondo tax groove 5 or 6 to the holroffenden Achsi w allage of the piston 2,4 with rod 3, a connection from the named inlet 25 or the annular chamber 18 to the relevant chamber 27 or 29 manufactures; and / or wherein said valve 19 is one-way loaded, for example by means of the fields 20, and in the other direction by the stronger one Pressure at the relevant time in the chamber 27 or 29 is loaded, and / or in which said valve 19 with stop 21,22, e.g. is equipped on the shaft 24 so that the valve 17 cannot push against the piston shaft 3, and / or in which the valve 17 is arranged in an installable valve holder 26, and / or, in which the Exhaust gases from the chambers via lines 29, 11 create a pressure in the inlet 25 promoting Chargers, for example Turbo 12, drive the charge air or the mixture into the inlet 25 and through the valve 17 into the relevant chamber 27 or 29, and / or, wherein self-acting inlet valves 9, 10, LEt deliver into all lines 11 from the outside or let in, and or, wherein the piston stroke is so long that the compression pressure in the chamber in question becomes so high that it becomes the self inflammation temperature is exceeded and therefore no mixture is sucked in, but Fuel through the relevant inlet = guide 16, 17 into the relevant chamber 27, 29 is promoted, and or, in which outer cover 8 backwards the piston 2.4 chambers close so that the exhaust gases do not escape froi, but a turbocharger 12 to feed, and / or, wherein at least one of the piston parts 2,4,3 with a Abge = distribution 7 is provided, of which the work of the Achsiulbe- "movement the piston 2,4 can be removed; oderi that the piston rod 3 is longer is, between the mentioned chambers 27,28 two Tronnewende 115,215 are arranged, which replace the central wall 15 and the relevant chambers 27 and 28 around the piston rod 3 close herutn, the named control grooves 5, 6 are arranged so that the relevant partition wall running, the relevant in the relevant partition anct 115, 215 arranged inlet channel 16, 17 at the corresponding time and axial position the piston assembly 2,3,4 connect to the relevant chamber 27 or 28 and also between said dividing turns a piston rod part 3 surrounding the relevant piston rod part Space 103 is arranged in which either means for taking off the power of the Piston rod 3, for example, are arranged according to Figures 51, 52, or these Arrangement, for example, by means of the shaft 2 with lifting disks 4 serves the two To twin pistons to run in parallel with other pistons that are substantially the same, or, which is used to set up a compressor or pump arrangement in this space 103, for example 46 to 49 or 51 and 52 or the like to decrease the Si = stung into one or more compressed air or pressurized fluid flows, for example hydrofluid flows to convert, and / or with this decrease and conversion by templates 40,43 or the like with curved surfaces 41,44 which meet the conditions of the equations correspond to FIG. 50, and / or in which pivot lever which reduces piston shoe friction 32, e.g.

are assigned according to Figures 46 to 49 with their parts and accessories, and / or, in which guides 63,64 for template carriers 62 are arranged, and / or, wherein means, for example 50,51,8,2,4,49 of the figures 51,52 or 123,223,323,126,120, 121,12 @ etc. of Figures 70 or 71 axially outside the piston 2, 4 or in the Spaces 103 are arranged between the separating disks 115,215 in order to abut the Free flight piston arrangement 2,3,4 on end walls 8, middle piece 15 or dividing walls 115,215 to prevent, so the stroke of the piston assembly 2, 3,4, even then forcibly to limit when the piston assembly voltage high inertia forces due to very high Axial movement frequency has the piston without such limitation of the stroke arrangement against the mentioned parts could throw, and / or, whereby by this Arrangement the axial stroke frequency of the piston arrangement 2,3,4 considerably or noticeably is increased beyond what has been achieved so far and / or in which the system is used is to a plurality of proportionally equal to each other promoting pressurized fluid flows to generate, and / or in which axially outside the end walls, the piston rod extension Elongations 333 have been run through, for example according to FIG. 67, external boost pressure chambers 100, 200 are arranged with outer pistons 202, 203 inserted therein, the air Record via inlets 204 and compressed or pre-compressed via outlets 205, 206 through lines via inlet one-way valves 19 into the relevant chamber 27 or 28 promote, (e.g. Figure 67 with valve 25, 19 according to Figure 68) and / or, in which the Motor only the housing 1 with the chambers 27,29, piston arrangement 2,3,4, outlet 29 and inlet 25, 19.

maybe with a turbocharger in between has to achieve a high performance to achieve with the lowest weight, and / or, with several such Motornn by Connecting rod and crankshaft 1 ″ 3, 2, 120 according to FIGS. 20, 71 forced to run in parallel will, and / or the crankshaft-connecting rod arrangement according to FIGS = ren 70,71 only at one end of one of the pistons 2 or 4 of the relevant engine 1,401,501 arranged to achieve high performance with low weight, and / or, wherein the crankshaft with pumping means 130 to 133, 134 to 137 or some of the same The same is connected, so that the system according to FIGS. 70 and 71 has a hydrofluid promotional combustion engine, for example, high performance with low Weight, can be used, for example, for the vertical ascent of hydrofoil aircraft It is also reported that the assumption that free-flight pistons with 10,000 double strokes can drive, as assumed in Figures 67, 68, no consideration of the inventor is, but that these assertions from the eighties from the VDI Nachrichten come.

Since the mass forces at 10,000 lifts are already a hundred times higher are, i.e. 100 times higher deceleration forces are required than with 1000 lifts at the same time, the inventor is somewhat suspicious of these messages. It was already the case in the second world war that we did not find out what was going on abroad happened and today it is the case that, for example, the average is not the slightest Has an idea of who invented the buzzing excavator, for example, right? Anyone who received practical people's aircraft patents two decades ago will get Mnd constructed, or who the power to weight ratio of the radial piston units to the hundredth Has reduced part. The more one is propaganda about miracle engines in the press exposed, which will then be called the engine of the century. In the current invention the performance comparison has been made, but the inventor holds stronger Fuses to prevent the free-flight piston from running against a cylinder cover, a central wall or a partition wall for useful as the pure control through gas cross-sections, if the 20,000 or 30,000 double strokes per minute are to be achieved, over reported by the VDI Nachrichten. Hence the protective measures in the current one Patent application, to which further additions may be submitted. After all, the deceleration forces for the free-flight piston must be at 30,000 rpm 900 rnal stronger than 1000 double strokes per minute.

The easiest to build nowadays is of the free-flight engines described Figures the execution according to Figures 70 or 71, or attachment of a crankshaft - Power take-off - arrangement at one end of one of the pistons of FIGS. 45, 67 or 68, because crankshafts and connecting rods can be bought cheaply as spare parts from car dealers to buy. Without a decrease in performance - make an arrangement on the free-flight piston units they don't make a lot of sense, as is evident from the inventor's mentioned USA patents.

Even if the power is removed electrically, it remains but a backup for high stroke frequencies of many 1000 double strokes per minute against one of the parts running against another. Therefor gives the current one Patent application Rn = haltpunkte and others may be possible in additional patent applications still to follow.

The Otto engine with water. Post-injection of Figure 72 with the P-V The diagram according to FIG. 74 now has some sense again because turbo charging is cheap today is possible. Originally at the US priority filing, the inventor assumed that the large volume expansion of the steam when the water is transformed into steam is to make an increase in performance possible if you use the heat to heat up takes the water into steam from the combustion chamber. In Figure 76 it was assumed at that time that this could lead to a lower air requirement. After the deliberations from the last few months that doesn't seem to be correct. The calorific value that the maximum amount of air the amber absorbs is not enough to absorb as much space Generate steam like the gas did. Therefore, the figure 72 makes sense in particular, if the engine has a higher air volume than with natural suction. Then there is the gradual water injection through inlets 47,48,49 of FIG. 72 occasionally expediently to reduce the gas temperature to cool.

This cooling then leads to a drop in performance. The injection agent for injecting water under high pressure for rapid evaporation accordingly small drops are available today through the parts of the pre-registrations and can be visited. The same applies to Figures 75 and 76, the Priority registrations for the current registration and one of the pre-registrations are. Here, too, it is gradual Water injection through inlets 65,66 and in Figure 78 the calculation formulas are given with which one the conveyor = amount of water through conical pumping elements of the inventor and his Partner can calculate. Details can be found in one of the pre-registrations.

With the current status of the investigations from August 1982, the inventor hawed the impression that the water injection should not be overdone because seems to go in parallel with it a considerable decrease in efficiency. Please refer the preliminary data in FIGS. 60 to 63. The water injection is no longer a technical difficulty today, since high pressure water pumps are included in the pre-registration of long service life are disclosed.

But only then and only as much water should be injected as is necessary to reduce TeXmperotur. Especially with turbo charging of the Engines. However, it is a means of the invention to reduce the losses due to water injection to be reduced considerably by the fact that the water to be evaporated is according to the invention Preheated in the exhaust gas to boiling temperature or it at all under considerable pressure preheated in the exhaust. Because then the proportion of warmth used to heat the water falls when injecting into the motor of Figures 40, 41, 56, 72 or 75 and the evaporation = warmth is then much lower. The efficiency of the motor with water injection then decrease significantly less than indicated in the diagrams of Figures 60 to 63, or even too, and the exhaust gas from the combustion chamber then nevertheless lowers its temperatures considerably. If not previously known, this is a lesson from the current one Patent application. Accordingly, FIGS. 72 to 76 then make sense again. (Figure 73 is described separately. The figure 73 serves to indicate the cylinders of the combustion = to make motors steadfast for higher pressures. The pressure chambers 78 are for this purpose or 79 or one of the same placed around the cylinder 76 so that the cylinder wall 76 is under approximately the same engine pressure from both sides, In any case, however, the pressure difference is lower than with the usual cylinder fn the free atmosphere.

The invention attempts to achieve the goals of FIGS. 72 to 76, for example, by determining the pressures in the combustion chamber, the cross-sections of the inlets influencing the combustion points and the flow rates of the compressed air, such as the fuel supply according to the teachings of the patent application or its mathematics, takes place, any additional water spraying lowers the temperatures, the water spraying can also take place in two-stroke or four-stroke engines according to Figure 72, but is done in such a way that the efficiency does not fall below that of the steam engine, in particular water after-spraying can be provided when the compressor is charged takes place so that a highly concentrated air supply enables a high calorific value introduction of fuel that the relationships described take place in the sense of FIGS. 60 to 63 or using the new mathematical formulas disclosed in the applications that the cylinder wall is surrounded radially on the outside by at least one, but preferably several, chambers 78 or 78 and 79, into which a pressure is introduced through line (s) 80, 81 that is substantially approximately that in the relevant part in the cylinder 75 prevails, the named chambers 78, 79 being or are arranged in a housing 800 surrounding the cylinder 76 that water injection is injected at different points relative to the distance from the start of combustion according to Figures 72 or 75, 76, 74 in order to generate water vapor, to take the heating from the hot gas and thereby add the steam volume, unfortunately with a loss of gas expansion capacity, however, to lower the gas temperature.

Figures 58 and 59 show a valve that is particularly useful when used in the star cylinder unit of FIG. 7 or the corresponding figures in one the advance notice, may gain importance. Because the aggregate of Figure 7 resp. de of the pre-registrations has the great advantage of the smallest dead space with a large one Realize delivery rate as a compressor.

The piston 26 is driven radially from the outside by means of the lifting rings of the invention radially inward or with connecting rods of crankshafts, which, like the cam ring, are driven in parallel.

In the process, a very large amount of air is created in the very small, almost dead space Central chamber 15 concentrated at high pressure. The danger of dussing the piston tips flying or bumping into each other is not very large, since the outlet valve 79, as described in the pre-registration, can be set to high pressure so that a strong braking or resistance against the inward stroke of the pistons 26 takes place before reaching the inner dead center position. At the high speeds, which the sliding shoes allow on the feeders and which presumably especially the crankshaft the figure 77 seems to promise, it is therefore worth striving for, also the aggregate the pre-registration, with which the figure 7 deals, even further to higher stroke frequencies to increase.

For this purpose, larger inlet cross-sections are useful for the inlet air, than they are previously provided in this unit with which FIG. 7 deals. Therefore, according to the example of the invention in FIGS. 58 and 59, a valve 84 is included Valve seat 85 of large cross-section and flow-favorable shape arranged that a face 181 forms which with the radius 81 of the piston 26 to the piston outer surfaces is shaped complementarily. Consequently, this arrangement reduces dead space or considerable Dead space in front of the valve, that is, between the valve head and the piston 26.

So that this system is operationally safe, the valve comes with a guide 93,94, which prevents the valve from rotating around its axis. In order to the end face always remains in the desired position relative to the piston 26. In addition, a strong arrangement 88 to 91 is arranged, with the valve against the pressure in the central space 15 is opened or controlled in an arbitrary and timed manner has been locked. The valve therefore helps to bring larger amounts of air into the central chamber 15 between the the several, at least three, pistons 26 to leave and therefore to leave higher stroke frequencies more rational.

The realization of the goal of FIGS. 58, 59, for example aimed at that after those figures one of the pre-registrations with de = ren improvement is concerned with FIG. 7 and after FIGS. 58, 5S, in which several Chambers, to the Dci game cylinder 8.26 star-shaped with axes in a common The cylinders meet in the middle, in the above-mentioned plane Cylinders piston 26 reciprocate and their reciprocation radially from en to parallel synchronism inward and outward by means of radially outwardly arranged Stroke disks or crankshafts and connecting rods is forced, in which the piston heads 80 inwardly directed end faces of such a shape that the innermost Dead center, the aforementioned front surfaces almost one another without any appreciable space in between and only a remnant of a chamber 15 of only a few cubic millimeters or cubic centimeters, so that the system as a compressor discharges almost all of the compressed air the interior space between the pistons, even with pressure from over 25 or more than 100 bar, without suffering any appreciable tolerance or friction losses and in which the housing and the inner chamber 15 have the outlet valve 79 at one end is assigned, but at the other end, a lot of air is efficiently allowed through The inlet valve 1 has a large cross-section, namely the valve 84 of FIGS. 58, 59 is arranged, for example, an end face 181 with the radius 81 of the piston outer faces has, so that this end face faces the piston outer faces without any significant dead space to let, nachren can, preferably under a conical seat 85, and / or, in which the valve 84 with a fuse and guide 93.94 against rotation is provided around the valve axis 184 so that the end face 181 does not twist view can and always remains parallel to the outer flacchen of the piston 26, and / or wherein the valve 84 is closed with a powerful push-on and lift-off device precisely in relation to the piston position of the piston 26 is provided controlled, for Example with the piston 92 between the pressure chambers 89.90 in the housing 87, which through Channels 88.91 are acted upon with high pressure fluid at precisely the same time, so that the inlet valve so firmly with the head 85 in its seats on the cylinder housing ô remains when the high pressure is formed in the inner chamber 15 that by the Valve closure 85 no air or even at high pressures in the inner chamber 15 No gas (not substantial) can escape, but the Vcnti lock is still in place 85 is shaped and dimensioned in such a way that large amounts of air are released during the evacuation stroke of the Piston 26 into which the central chamber 15 and the cylinder can flow quickly, about high stroke frequencies and very high pressures with almost no load and dead space To realize operation of the aggregate, for example, also in order to thereby achieve a rational To create a motor according to the invention, which is certainly sufficiently high pressure in the antechamber to the combustion chamber, for example in chambers 27,200 of the figures 40.41; or 63, 64, 67 of FIGS. 53 to 56 or 64 of FIG. 75 or 8, 9 of the Firjur 1, which has such a high compression temperature that it is certain burns the fuel quickly and almost completely and, if necessary, one Overpressure above that in the combustion chamber 5, which supplies a strong forced flow through the end of the gap in the nozzle or focal point of the figures concerned generated.

Figure 77 also deals with the desired increase in performance of internal combustion engines per given weight. The crankshafts of Figure 64 for example run reliably up to about 10,000 rpm with hydrodynamic lubrication. Whether they still run safely at even higher speeds is currently not sufficient known. The application is therefore based on the idea that the connecting rod of such Crankshaft weighs only about 600 grams and one with the heaviest part of about 60 mm diameter per turn. Thereby the centrifugal force already F = m # ²r so about 19 kilograms at 1000 revolutions per minute. These The hydrodynamic bearing can easily carry a load of around 20 kg. At 10,000 rpm, the centrifugal force, however, is ten times higher since it is with the The square of the number in circulation is growing, already 1o times 10, i.e. a hundred times as large. That 2000 kg of centrifugal force are then already carried on about 9 square centimeters Need to become. (9cm2 storage area.) So you already have 200 kg load per square centimeter, w s not too high for hydrodynamic bearings, but considerable is. Even at 12,000 rpm, the bearing pressure would be around 300 kg per cm2. The speed increase There are therefore limits. / Therefore, Figure 77 of the invention seeks to be large to arrange hydrostatic pressure fluid bags at the points on the crankshaft where the centrifugal force becomes effective. The pressure = fluid pockets 86, 87 are used for this purpose the channels 85,88 filled with hydrostatic pressure fluid. You can now according to the invention also control the pressure in the mentioned pockets depending on the speed.

So you can relate to any pressure between 0 and 500 bar, for example simply guide it into the pressure pockets in FIG. 77. In this way, the figure aims at that The speed of the crankshaft can still further increase zL, or the 13 £ 'is allowed to (~ to lift counterweights by moving the counteracting pressure fluid pockets accordingly placed and expanded. So it should be possible to reduce the speed by a few to increase a thousand rpm, which is very important for the increase in performance of engines for the vertical ascent of aircraft with inexpensive propulsion engines. At 14,000 rpm, for example, the centrifugal force of the connecting rods mentioned is around 4000 kg you can with appropriate Still carry pressure fluid bags 86.87.

The aim of Figure 77 attempts the invention thereby, for example to meet that a crankshaft 483, for example according to the figure 77 is designed in this way is that a channel 85 pressurized oil in arranged in the crankshaft pressure fluid pockets 86.87 conducts, with the pressure fluid bags 86.87 the storage areas in the storage and are too open in the connecting rod and are angularly distributed around the crankshaft, that the pressure fluid pockets are exerted in the direction of the crankshaft and connecting rods Forces, especially centrifugal forces, act in opposite directions and these forces balance or partially balance, the pressure in the lubricating fluid automatically should be controlled in dependence on the speed and the pressure fluid pockets are placed and dimensioned accordingly that the counterweights of the previous Crankshafts for example can be wholly or partially saved and / or the Pressurized fluid bags carry and store the crank shaft and the connecting rods 84 so well that the crankshaft 483 or 83 can rotate at high speeds or higher speeds possible than has been possible with previous hydrodynamic bearings or roller bearings was.

The priorities of those Voronneldurten in Claimed, in part or in full, that are less than a year old. To the Example that of the main application 31 35 675 from 9.9. 1981 or an application dated same day and the pre-registrations of July 13, 1982, whose file number is not are known because the certificates of acceptance were lost, as well as those of the registration from late August 1982 and possibly one or some US priorities. The exact File numbers will be submitted later when they are known and then reported, to which main patent application this application is to be an additional application.

L e r s e i t e

Claims (4)

P AT E N T A N S P R U C H E: 1.) Heating system with a combustion chamber and successively delivering upstream compressor chambers for the delivery of Air into the combustion chamber and with a device to prevent a sharp drop in pressure in the combustion chamber, characterized in that the combustion chamber with a guide arrangement 1 for the regulated supply of a Solid fuel, fuel rod, fuel band,, 4, is provided and the The pressure in the combustion chamber is kept so high that the fuel rod ignites by itself burns and a continuous flame in the focal points 5 at continuous Maintain compressed air supply. 2,) plant still claim 1, characterized in that said Combustion chamber the combustion chamber of an internal combustion engine with external combustion and expansion chambers downstream of the combustion chamber, characterized in that that said fuel rod 4 is a solid fuel, for example cleaned or pressed Coal is in the form of a stick or ribbon, and burns continuously of the fuel rod in the compressed hot air supplied to the combustion chamber Power output of an engine is used. 3.) Plant according to claim 2, characterized in that the fuel rod 4 a speed control for determining and controlling the feed speed is assigned and / or the fuel rod is sealed in its guide against gas losses is. 4.) Plant according to claim 1, characterized in that a liquid piston 40 is arranged such that a chamber between compressible Kanischen ring = elements is connected to a compressor or expansion chamber 27 and a Liquid in the chamber 40 then penetrates into said chamber 27 or they left and their volume increased or decreased when the ring elements 33, 35 compress or expand. 5.) Plant according to claim 4, characterized in that said Chamber 27 contains a cover with inlet and outlet valves 29,30 and as a compressor or expander for air or gas is used, said water flask or fluid piston 40, that is to say the amount of fluid 40 below or in the chamber the chambers = lumen compressed or expanded with gas or air in it compress or expand. 6.) Plant according to claim 1, characterized in that the compressor continuous and. with as little fluctuation as possible, compressed hot air passed through a nozzle 6 with a cross-sectional shape and a cross-sectional thickness which corresponds to the cross-sectional shape and thickness of the fuel rod 4, or the The thickness and cross-sectional shape of the focal strip 4 corresponds to that of the nozzle 6, so that the fuel thickness 18 and the nozzle thickness 19 at corresponding speeds of the fuel rod and through the nozzles are coordinated so that a ideal complete combustion of solid fuel from the stick or tape 4 takes place. 7.) Plant according to claim 6, characterized in that the thickness 18 and the feed speed 12 of the fuel rod 4 of the shape, thickness 19 and Flow rate and pressure is appropriately adjusted, as well as the rod movement direction = device and the nozzle direction, such as the distance between the piston 4 and the nozzle 6 for vol constant and perfect combustion grooves = are matched to each other. 8.) Plant according to claim 1, characterized in that the piston 26.40 of a compressor or expander, an inlet valve 80, 67 for the purpose of filling the working chamber 15, 50, 51, 52 through the piston 53, 54, 55, 26, 40, so that an installation gas flow is achieved through the working chamber and the face of the piston head or valve head, 0, to the face of the outlet valve 63.15 is adapted complementarily to dead space in the said Avoid working chamber and an engine with high external combustion To create pressure and efficiency. Plant according to claim 1, characterized in that in the combustion chamber a rotating fluid bath 23, in particular a rotating water bath 23, is arranged is. 10.) Plant according to claim 2, characterized in that after Combustion of water under high pressure and with fine atomization in the combustion chamber 20 is injected and vaporized to the temperature of the gas after combustion to a usable temperature for the parts and valves, or by Evaporation of the water has a special effect on the system or the motor to achieve. 11.) Plant according to claim 1 or 2, characterized in that as Valves balls or rollers are used, the piston or inlet valve heads Complementary faces have 1 e or the aforementioned balls or rollers Valves are rotated, rolled, and / or oscillated. 12.) Plant still claim 1, characterized in that as Verdlchtersätz Promote several first cylinders one after the other in second cylinders, for example the first cylinder 50,51,52 in the second cylinder 56,57,58 via valves 63 between promote the first and second cylinders, this promotion under one first high pressure takes place and the second cylinder at the evacuation tube with this first high pressure to be filled then one after the other from the named = th second cylinders 56,57, SS out high pressure air with a second, higher, high pressure To be conveyed via valves 64 into the common collecting line 65 and forwarding 66. Attachment, for example, according to one of the claims of the main application , one of the pre-registrations or this registration, characterized in that between two coaxial, axially spaced cylinders or chambers 3, 33, 13, 14 for example according to FIGS. 13 to 39 and 79, 80 or one or some of these Fi = guren, a centrally mounted shaft 2, 18, for example in bearings 12, around a to the common socket 25 of said chambers 13,14, perpendicular and through said common axis laid shaft axis 26 is rotatably supported and axially a central recess 16 by the distance "e" = 6 from the shaft axis with the radius "R" = 7 formed lifting disks 4 with cylindrical about the eccentric axis 23 Fuehrungsflaechen 8 of radius "R" around the said eccentric axis 23 is arranged are, which are the inner surfaces 9 of two in the piston 1,11 in its at a distance 19 with a radius of 100 designed swivel bed surfaces 24 with the piston shoe outer surface = chen 10, also with the mentioned radius 100, pivotable inserted piston shoes 5.55 touch and / or guide keonnen, the said piston 5.55 in both of the chambers 13, 14 he = stretches 2 as well as in them sealingly along the named common = the same axis 25 achsiol reciprocable, and said piston in its ocisiulen middle forms a hollow space 27 through which part of said shaft 2.18 extends and is limited by at least two connecting webs 21.22 is that connect the two piston heads 1 and 11 to one another and thereby both Piston heads 1 and 11 are held together in a non-positive manner. 14.) Plant according to claim 13, characterized in that said Lifting disks 4 protrude in places over the outer surfaces 28 of the said piston 1.11, said connecting webs 21, 22 enter said recess 16 and Are arranged between the two mentioned lifting disks 4, 15) Installation according to Claim 13, characterized in that the said external surfaces dose 28 of the piston 1.11 abut the inner surfaces 29 of the chamber housing 3.33 in a sealing manner = move or slide and thereby close the mentioned chambers 13, 14, as well as during their axial movement along the named common axis 25, that is to say at qem the reciprocals mentioned, increase in relation to each other in the inverse proportion and zoom out. Plant according to claim 13, characterized in that said Axial movement of the piston 1.11 either through fluid pressure in the named chambers 13, 14 or by the movement (rotation) of said cam disks 4 or by both are generated or managed. 17.) Plant according to claim 13, characterized in that said Lifting disks 4 with axial continuation which is cylindrical about the said shafts axis 26 18 are provided and attached to these on the shaft 2, said Fort = sets 18 can also carry the bearings 12 mentioned at the same time, or are stored in them. 18.) Plant according to claim 13, characterized in that at least one of the chamber housings 3, 33 is provided with a removable and attachable cover 333 is to the Eivifuehrung of said piston 1.11 in the relevant chambers 13.14 to enable. 19.) Plant according to claim 13, characterized in that the piston 1.11 has a length between its two axial ends 24 that is only slightly shorter, than the distance between the chamber floors 30 reduced by the stroke of the piston is and the bulge according to claim 13 is arranged for that despite the The piston ends 24 never come into contact with the chamber bottoms 30, as mentioned only by a small distance can butt, because the support of the piston shoe surfaces 9 and 10 on the swing = bed surface 24, or on the guide surface 8 prevent this. 20a) system according to claim 13, characterized in that several Chamber sets 13, 14, in chamber housings 3, 33, 133, 233, for example according to the figures 19,20,33,34 are assigned to a common housing 15 and are in common on the same Axes of reciprocating pistons are arranged with corresponding piston heads 1.11, wherein at least one of the said pistons with at least 4 connecting webs a21, 321, 222, 322 is provided, for example, according to FIGS. 20 to 24 and the aforementioned at least four connecting webs to the side of the two connecting webs in between 121,122 of another of said pistons 1,11 are arranged. 21.) To position according to claim 13, characterized in that, for example According to Figures 49 to 27 a given = if connecting webs 121, 122 to the piston heads 1.11 of said piston fastening pin 34 into a recess 31 of a piston shoe 5 engaging, is arranged. 22.) Plant according to claim 13, characterized in that for example According to Figures 28, 29 or 30 to 32, several pairs of lifting disks 4,444,104,204 a common = seed shaft 2 in the direction of the spacing "e" of the Exzenteraeh sen 23 are arranged rotated angularly to each other at the same angles, 23.) A nlage according to claim 13, characterized in that, for example, according to the figures 33 to 37 a pressure line 45 is arranged through a chamber housing 3 and the Piston 1,11 with at least one groove 48 for connection to the mouth of the relevant Pressure line 45 is provided and also given = if bores or channels 47,49 contains the fluid from said line 45 in pressurized fluid pockets 38,39 a piston or piston shoe 5 guide. 24.) A nLage according to claim 13, characterized in that the piston heads are provided with recesses 50, 52, e.g. according to Figures 38, 39, in the holding fingers 51.53 of connection = webs 421,422 or 521,522 engage and / or, that a piston head cover 55 parts of said connecting webs and the piston heads 1.11 encompasses and attaches it, or is attached to it. 25.) Plant according to claim 13, characterized in that in the mentioned piston 1,11, in the respective piston head 1,11, for example after 79, cavities 57 are arranged, in which inner pistons 56 the piston shoes 5 supporting, are reciprocable, said inner piston 56 by compression springs 58 inside the piston heads 1.11 inwards, i.e. towards each other, are pressed, for example by the change in the rotation of the mentioned shaft 2 and the lifting disks 4 Distance a l of Figure 80 to equalize and / or, the pressure of said Springs 58 is held stronger than that which may occur on the piston 1.11 Mass forces 26.) Plant according to claim 1, characterized in that the fuel first powder form with or powder with liquid, for example with a little water, is mixed and is fed under pressure to a nozzle, which is cross-sectioned is so tight that the powder compacts into a tight powder under the pressure, especially to a flat cross-section with a larger width than the thickness of the cross-section and the powder is in the cross-sectional shape of a thin threefold, from which @uese is pressed. 27.) Plant according to claim 1, characterized in that the cross section of the fuel rod is wider than it is thick and filled with hot air Duese enters, the cross-section of which is thinner than it is wide. 28.) Plant according to claim 27, characterized in that the fuel belt in addition to other fuel belts, is guided through appropriate cross-sections, so as a whole there is a wide, thin supply of fuel into the Combustion chamber takes place. 29g) Plant according to claim 1, characterized in that said Combustion chamber is that of an internal combustion engine with external combustion into which a The compressor blows in hot, compressed air and the combustion chamber relaxes is downstream, into which the combustion chamber delivers its hot gases and the said Expander drives the compressor and, in addition, relaxation work poured off to the outside, for example according to Figures 40 or 41, wherein the or the Compressor 2, 3 is connected to the inlet 200 of the combustion chamber 5 and the outlet 10 from the combustion chamber to the explosion chambers e.g. 13,14,15 periodically one after the other verbun -den, so that the working elements, for example pistons 16, 17,18 after each other with hot gas from the combustion chamber 5, for example via a control or valve arrangement 12 with inlet means 10 and outlet means 11 are periodically acted upon to perform their work and expansion hub and for example over Connecting rods and a crankshaft drive the compressor elements 19 to 24 and above In addition, work through the crankshaft out of the housing 30 to the outside, 30.) Plant according to claim 29, characterized in that a valve 12 is arranged with which all entrances to all expansion chambers e.g. 13 to 15, are closed so that when starting the engine or its crankshaft 1 by the compressor e.g. 2, 3, highly compressed hot air is accumulated in the combustion chamber 5 which is blocked from escaping into the expander, whereby the air pressure rises and the temperature rises so high that the fuel itself ignites and burns in it. 31.) Plant according to claims 29 or 30, characterized in that After the fuel has been ignited, a passage to the venting device is open or automatically is opened, for example by means of a pressure or temperature sensing means, e.g. 7th 32.) Plant according to claim 31, characterized in that between the ignition chamber part 27 of the combustion chamber 5 and the tensioning part 13 to 15 have a lock 6 is arranged, the after exceeding the ignition temperature causing Zuenddruckes in front of the aforementioned lock 6 by an ei = nc tacrS loaded tactile piston 51 and then line the pressure under a lifting element 666 swiftly and in accordance with the delivery pressure from the compressor and the gas intake by the expander (13-15) or by a similar effect System is opened, for example according to Figure 41. 33.) Plant according to claim 29, characterized in that the fuel is stored in a chamber 44, which through a line 144 is a non-combustible Gas is supplied with a pressure equal to that of the combustion chamber 5 or that of the compressor supply is equivalent to. 34.) Plant according to claim 29, characterized in that the fuel 45 is a band with a wide thin cross-section and a conveyor set, for example a Pair of rollers 8, arranged is that the fuel is under seal as tape or Belt belt 45 introduces the nozzle 27 in the speed, those to be burned with the desired air, receive "lombda" in the hot Air in the said nozzle 27 is required. 35.) System according to claim 29, characterized in that the focal point 27 a nozzle-thickness adjusting element or nozzle cross-section adjusting element 46 is assigned, for example, according to FIG. 41, with which the cross section of the focal point or Duese 27 can be changed and thereby the burning process, the distance of the Fuel or the air speed or the air pressure that Coming from the compressor can be influenced in order to achieve an optimal combustion effect of the fuel 28, 45 in the combustion point 27 or in the combustion chamber 5 to effect. 36.) Plant according to claim 29, characterized in that before Relaxers, e.g. 12, 13 to 15, a dirt or foreign body separator, e.g. 42-44,55,59,60 with rotor drive 41, which is interchangeable = arranges may be and / or added to or removed from the system by means of the holder 40 can be, if so desired. 37.) Plant according to claim 29, characterized in that it has a Crankshaft 1 contains the valves, for example the Rotor valve 12 and the compressor = part, e.g. 3, 4, 19 to 24 drives and / or the Compressor part supplies a higher air pressure in front of the combustion point 27 than in the Combustion chamber main part 5 is present, so that the hot air under excess pressure through the nozzle 27 is pressed and a beSOn -compressed and hot air is available there is where the fuel tip enters the air, or the fuel dust enters it is pressed in. 38.) Plant according to claim 29, characterized in that, for example According to FIG. 54, fuel mixed with powder or powder and water from one line 68 under compression in a nozzle 69 with a narrower cross-section into the focal point 72 is pressed. 39.) Plant according to claim 29, characterized in that the fuel rod or the fuel belt 28 without first passing through the combustion chamber 5, into a narrow one Duese 64 is forced into the hot compressed air coming from the compressor from the inlet 63 larger Q cut into the narrower cross-section of the nozzle 64 is initiated. 40.) Plant according to claim 29, characterized in that for example air formed according to Figures 54 and 55 = inlets 64, fuel inlets 69, Nozzle noses 70 and 71 are arranged and a nozzle cross-section adjusting means 65 by means of a Leitfiaeche 66 the nozzle cross-section at nose 71, at cross-section 73 or at nose 70 or at several of these locations as desired or according to automatic Control expands or narrows, especially a thin, wide cross = Section 73 according to FIG. 55 expanded or narrowed by a thin, wide flame with highly perfect combustion. 41.) Plant according to claim 29, characterized in that between the combustion chamber 5 or 65, the air inlet 67 and the fuel supply duct 76, for example, according to FIG. 56, the noses 71, 181, 281 forming the nozzles with the End point 85 are arranged and these noses come closer to one another or from one another can be removed, for example using eccentric pressing parts 78.79 and 82.83 in rooms 77 and 84 beyond thin walls that yield under eccentric action 80, 81, which carry or form said noses 181 and 281. 42.) Plant according to claim 29, characterized in that the combustion chamber 5 is extended by means of a channel 65 to behind the engine and there under him a removable part 88 is arranged, which collects the dirt or foreign bodies position 89 contains, from the bottom of which a forwarding channel 90 to an intermediate channel 91 leads in the combustion head, from where the hot working gas then exits through the combustion chamber 92 lying to the relaxers, with the removable part 88 on a holding surface Burner sits and is held on it, for example by means of a holder 93, or while the vehicle is in motion by means of tensioners 94,95 and Guide plate or retaining plate 93 can be pushed out and replaced by a new one can when the dirt collection system has become full, as for example in Figure 57 described. 43.) Plant according to claim 29, characterized in that in it Compressor systems are used, which have low dead space and a high degree of conveyance have high pressures, for example attachments after one of the pre-registrations or after of this patent application, so that even at pressures over 20 bar to over 100 Bar still high-efficiency compressed air to promote high efficiency of the engine. 44,) Plant according to claim 29, characterized in that a water injection system 86 according to Figure 56 or one according to Figures 72 to 76 a motor with outside = combustion chamber or a gasoline or diesel engine using the lessons or math assigned to this patent application. s) Attachment, for example according to one of the claims of the main application , one of the pre-registrations or this registration, characterized in that one chamber through which fluid flows, for example chamber 1 according to FIGS. 42 to 44, which for example are not just chambers of a hydraulic pump or a hydraulic motor need, but also chambers or cylinders of a compressor, compressor, gas engine or can be decelerator or an internal combustion engine, such as for For example the cylinders 1, 2,3, ins to 15 of the compressors or expander of the figures 40,41, one stored in a bed 32, with its outer surface 31 in the named Bette rotatable circulation valve 12 upstream or downstream or upstream and downstream - Is ordered, the one cylindrical outer surface 31 as a sealing surface for the seal has on the Bettflaeche 32 and dfe has a radius which is the radius of the neighboring Can correspond to the piston head, so where the chamber 1 is preferably a piston 4 contains, the head of which is secured against rotation, to the named outside = surface 31 has complementary front surface 5 with the same radius, the said valve Contains inlet channels 10 and outlet channels 11, and characterized in that the valve for the purpose of good sealing with a part of the outer surface 31 against the Bed area 32 is pressed. 4s) Plant according to claim 41, characterized in that said Valve 12 has internal cavities 13 or 29 that can be used by cooling fluid, such as Air or water may be flowed through, and / or that said valve means an axial drive, e.g. 33,34,35,36,37,38,39 periodically moved axially, i.e. is oscillated or reciprocated, so that the rotary motion with an axial motion for the purpose of self-cleaning the sealing surfaces 31,32 or for the purpose of self-sealing the mentioned sealing surfaces 31,32 overlaid, and / or, in which a channel 13 with openings 14 is arranged for the purpose of flushing said chamber with cooling air, and / or, wherein said chamber is a cylinder in which a piston 4 runs, which at its lowermost layer releases slots 3 in the chamber wall 2, so that the exhaust gases escape from the chamber through these slots, and / or in which the exhaust gases pass through the outlet channel 11 and 9 are conducted, and / or, in which the channel 9 in the chamber head 27 interacting with the channel 11 in the valve 12 under pressure or running air, the chamber 1 temporarily flushed with cooling gas or cooling air or the exhaust gases through the duct element 3 drives out of the chamber 1, and / or that the valve 12 is diametrically opposite the inlet channel 8 in the valve head 27 and the inlet 106 in the chamber 1 a pressing arrangement is assigned, which consists of two or more pressure pistons 16 in ßnpreSszylindern 15, whose contact pressure is directed to said channel 8 and inlet 106 and which are axially offset parallel to the axis 112 of the valve 12, so that one of the Pressure piston on this side and the other on the other side of the channel 8 and 9, as well as the chamber inlet 106 lies and thereby an uninterrupted part of the outer surface 31 of the valve 12 touch, and / or that pressure fluid e.g. through channels 18 into the pressure chambers 15 is passed, this lubricating fluid can be that over arrangements a which contains advance reports with the gas pressure in channel 8 and inlet 106, but can be separated from these gases with the arrangement of the pre-registration, and / or, that the chambers 15 and piston 16 are dimensioned and directed so that the outer surface with one the rotation and / or axial movement of the valve 12th can slide without high friction on the bed surface 32 and thereby seals well against it, so that no gas or fluid escape from the chambers or spaces assigned to them can, or escaping fluid is a minimum, and / or that in the valve head 27 a sloping surface 24 of a chamber 19 is arranged on which a sealing block 20 with its bearing surface 25 rests, and / or that the said sealing block is a Sealing surface 120 is formed which is complementary to the outer surface 31 of the valve 12 is, so a partial cylinder surface 120 forms with the radius that the outer surface 31 of the valve 12 has, and / or, with the relevant sealing block in the valve housing assigned, a pressing piston 21 in a pressing chamber 22, which is by line 23 filled with pressure fluid rn0g, is arranged, which on the pressure block 20 presses and this with the surface 25 on the surface 24 and with its sealing surface 120 on the corresponding part of the outer surface 31 of the valve 12 presses, so that the said sealing surface of the block 20 the relevant passing rotating channel 10 or 11 of the Ven = tiles 12 closes and seals when this is with the channel 8 is in connection, and / or in which such a number of sealing blocks 20 with associated piston 21 and chambers 22 is arranged, as piston 16 is the valve 12 are assigned, and, or that the Kloetze 16 have the same axial box relative to the valve axis 112, like the aforementioned pressing plugs 16. 41.) Attachment, for example, according to one of the claims of the main application , one of the pre-registrations or this registration, characterized in that doss the Plant in substance a double free-flight piston engine, for example according to FIGS. 45 to 52 or 67, 68, 70, 71, in which two chambers 27 and 29, the are separated from one another by a central wall 15, two pistons 2.4, which by a Piston rod 3 are firmly connected to one another, which seal the central wall 15 penetrates, oscillates, i.e. reciprocates or back and forth in an axial direction run when fuel is supplied to the respective chamber through inlets 25,16,17 and is ignited in the compressed air in the relevant chamber, and, in which Control cross-sections axially fixed relative to or on the piston, for example as Grooves 6 and 6 are arranged in the piston rod 3, through which the relevant Chambers through the at least one central wall 15 with air or a mixture of fuel and air are filled and outlet channels 29 are present, from which the gases, their Work on the relevant piston 2 or 3 during the relaxation in the relevant Chamber have given up, can escape. Plant according to claim 43, characterized in that in said Central wall an inlet 18,25 is arranged, in which a check valve 19 gas in the annular chamber 18, but does not let any out or back through the valve 19, and that the relevant control groove 5 or 6 for the relevant axis position Piston 2.4 with rod 3, a connection from the named inlet 25, respectively. the annular chamber 18 to the chamber 27 or 29 in question produces; and / or, in which the said valve 19 is one-way loaded, for example by means of the spring 20, and in the other direction due to the stronger pressure at the relevant time in the Chamber 27 or 29 is loaded, and / or wherein said valve 19 with a Stop 21, 22, e.g. is equipped on the shaft 24 so that the valve 17 does not counteract can push the piston skirt 3, and / or, in which the valve 17 can be installed in a Valve holder 26 is arranged, and / or, wherein the exhaust gases from the chambers over Lines 29, 11 pressurize the inlet 25 conveying loader, for example turbo 12 driving the charge air or the mixture into the inlet 25 and through the valve 17 into the relevant chamber 27 or 29, and / or, wherein self-acting inlet valves 9, 10, supply air from outside into the lines 11 or let in, and or, wherein the piston stroke is so long that the Compression pressure in the chamber in question is so high that it reaches the self-inflammatory temperature ueberschetztbund therefore no mixture is sucked in, but fuel through the The relevant introduction 16, 17 into the relevant chamber 27, 29 is promoted, and or, in which the outer cover 8 closes the piston 2.4 chambers at the back, in order not to let the exhaust gases escape freely, but to feed them to a turbocharger 12, and./ or, in which at least one of the piston parts 2,4,3 has a discharge part 7 is provided, of which the work of the Achsialbe = movement of the piston 2,4 can be removed. 49.) Plant according to claim 44, characterized in that the piston rod 3 is formed longer, between the said chambers 27,28 two partition walls 115,215 are arranged, which replace the central wall 15 and the relevant chambers 27 and 28 close around the piston rod 3, the control grooves mentioned 5.6 are arranged so that the partition wall in question totaling the relevant in the respective separating and 115, 215 arranged inlet channel 16, 17 to the corresponding Time and axial position of the piston assembly 2,3,4 with the relevant chamber 27 or 28 connect and also between the mentioned separations were one of the relevant Piston rod part 3 surrounding space 103 is arranged in which either means for Decrease in the power of the piston rod 3, for example according to FIGS. 51, 52 are arranged, or this arrangement for example by means of the shaft 2 with lifting disks 4 serves to make the two pistons essentially the same for parallel running with others To force piston, or, which is used in this space 103 a compressors or Pump arrangement, for example, according to FIGS. 46 to 49 or 51 and 52 or the like for acceptance stung in one or more compressed air or pressure fluids Streams, for example hydrofl u idstroeme convert, and / or with this decrease and conversion using templates 40, 43 or the like with curved surfaces 41, 44 takes place which correspond to the conditions of the equations of Figure 50, and / or wherein Kolbenschuhre ibung reducing pivot lever 32, z. B. are assigned according to Figures 46 to 49 with their parts and accessories, and / or, in which guides 63,64 for template carriers 62 are arranged, and / or, wherein means, for example 50,51,8,2,4 49 of the figures 51,52 or 123,223,323,126,120, 121, 128 etc. of FIGS. 70 or 71 axially outside the pistons 2, 4 or in the Spaces 103 are arranged between the separating disks 115,215 in order to abut the Free-flight piston arrangement 2, 3, 4 on end wall 8, middle piece 15 or dividing walls: de 115,215 to prevent, so the stroke of the piston assembly 2, 3,4, even then forcibly to limit when the piston assembly voltage high inertia forces due to very high Axial movement frequency has the piston assembly without such limitation of the stroke could hurl against the parts mentioned, and / or, with this arrangement the axial stroke frequency of the piston arrangement 2,3,4 considerably or barely over what has been achieved so far is increased? and / or in which the facility is used is, to a plurality of proportionally equal to one another promoting pressure = fluddstroeme to generate, and / or in which axially outside the end walls, the piston rod extensions 333 have been run through, for example according to FIG. 67, boost pressure outside commern 100, 200 with outer pistons 202, 203 immersing therein, the air through inlets 204 take up and via outlets 205, 206 compressed or pre-compressed by Feed lines via one-way valves 19 into the relevant chamber 27 or 28, (e.g. Figure 67 with valve 25, 19 according to Figure 68) and / or, in which the motor only has the Housing 1 with the chambers 27,29, piston assembly 2,3,4, outlet 29 and inlet 25.19 as possible with a turbocharger in between, in order to achieve a high performance to achieve the lowest possible weight, and / or, with several such engines by connecting rods and crankshaft 123,223, 323,126 according to Figures 70,71 are forced to run in parallel, and or the crankshaft-connecting rod arrangement according to the Figu = ren 70,71 only at one end of one the piston 2 or 4 of the engine in question 1,401,501 arranged to high power to achieve with low weights, and / or, in which the crankshaft = with pumping means 130 to 133, 134 to 137 or some of the same is connected so that the System according to FIGS. 70 and 71 forms an internal combustion engine which promotes hydrofluid and which For example, high performance with low weight, for example for vertical ascents i eg von Traaf 1 uege 1 aircraft can be used. 56.) Attachment for example according to Figure 7 or one of the pre-registrations and according to FIGS. 58, 58, in which several chambers, for example cylinders 8.26 The cylinders are arranged in a star shape with axes in a common plane meet in the middle, reciprocating pistons 26 in said cylinders and whose reciprocation radially from en to parallel synchronism inward and exaerts by means of hub disks or crankshafts and connecting rods arranged radially on the outside Is forced, in which the piston head 80 inwardly directed end faces of have such a shape that at the innermost dead center the face surfaces mentioned without significant space almost touching each other and only a remnant of the chamber 15 of only a few cubic millimeters or cubic centimeters, so that the system as a compressor, extract almost all compressed air from the interior between the pistons can, even with pressures of over 25 or over 100 bar, without significant dead space or to suffer frictional losses and in which the housing and the inner chamber 15 although the outlet valve 79 is allocated at one end, but a lot at the other end Air can pass through efficiently, namely an inlet valve with a large cross-section the valve 84 of FIGS. 58, 59 is arranged, which for example has an end face 181 with the radius 81 of the piston socket surfaces, so that this front surface is to leave the piston outer surfaces without substantial dead space, can, preferably under a conical seat 85, and / or, in which the valve 84 with one Securing and guiding 93,94 is provided against rotation around the valve axis 184, so that the front face 181 can not twist view and always parallel to the Outer surfaces of the piston 26 remains, and / or in which the valve 84 with a strong pressing and lifting device in terms of the ratio for the piston position of the piston 26 is provided in a controlled manner, for example with the piston 92 between the pressure chambers 89.90 in the housing 87, which are timed by channels 88.91 precisely acted upon with high pressure pressure fluid so that the inlet valve so firmly with the head 85 in its seats on the cylinder housing 8 remains when the high Pressure is formed in the inner chamber 15 that through the valve closure 85 as well at high pressures in the inner chamber 15 no air or no gas (substantially not) can escape, but nevertheless the valve closure 85 is shaped and dimensioned in this way is that large amounts of air during the ejection stroke of the piston 26 into the middle chamber 15 and the cylinder can flow quickly to high and very high stroke frequencies To achieve prints with almost loss-free and dead space-free operation of the unit, for example, also in order to create a rational motor according to the invention, the certainly sufficiently high pressure in the antechamber to the combustion chamber Example in de.n chambers 27,200, Figures 40,41; or 63,64,67 of the figures 53 to 56 or 64 of FIG. 75 or 8, 9 of FIG. 1 to produce the so high compression temperature has that this will certainly use the fuel quickly and almost completely = burns and possibly an overpressure above that in the combustion chamber 5 supplies, a strong forced flow through the narrow gap in the nozzle or burning point of the figures concerned. Attachment, for example, according to one of the claims of the main application , one of the pre-registrations or this registration, characterized in that the pressures in the combustion chamber, the cross-sections of the inlets influencing the combustion points and the velocities of the compressed air, such as the fuel delivery according to the teachings of the patent application or its mathematics, possible subsequent water injection the temperature lowers, with the water injection also in two-stroke or four-stroke Motors according to Figure 72 can be done, however, so happens that the efficiency does not drop below that of the dome machine, especially water spraying then can be provided when the compressor is charged, so that highly concentrated Air supply allows a high calorific value introduction of fuel that the described conditions in the sense of Figures 60 to 63 or using the new mathematical fortunes disclosed in the applications. 52.) The system according to FIG. 73, used in particular for cylinders according to one of the claims of the registration or one of the pre-registrations, characterized that the cylinder wall radially outside of at least one, but preferably several, chambers 78 or 78 and 79 is surrounded by line (s) 80,81 a pressure is introduced which is substantially similar to that in the relevant part prevails in cylinder 75, said chambers 78,79 in one of the cylinders 76 surrounding the housing 800 is or are. 53.) Arrangement according to claim 47, characterized in that water Injection at different points relative to the distance from the start of combustion is injected according to Figures 72 or 75,76,74 to generate water vapor, to take the heating from the hot gases and thereby the steam volume to add up, unfortunately with loss of gas s expansion capacity, but to the gas temperature to lower. 4.) Attachment, for example, according to one of the claims of the main application , one of the pre-registrations or this registration, characterized in that a Crankshaft 483 is designed, for example according to FIG. 77, in such a way that a channel 85 conducts pressure oil into pressure fluid pockets 86,87 arranged in the crankshaft, whereby the pressure fluid pockets 86, 87 open to the bearing surfaces in the bearing and in the connecting rod and are angularly distributed around the crankshaft so that the pressure fluid pockets in the direction of the force exerted on the crankshaft and connecting rod, in particular Centrifugal forces act in the opposite direction and balance these forces or partially off = balance, whereby the pressure in the lubricating fluid is automatically dependent should be controlled by the speed and the pressure fluid bags placed accordingly and are dimensioned that the counterweights of the previous crankshafts for example can be completely or partially saved and / or the pressure fluid pockets the crank shaft and the connecting rods 84 support and support so well that the crankshaft 483 or 83 with it high speeds or higher speeds possible than with previous hydrodynamic bearings or roller bearings was possible.