STORAGE-REGENERATIVE INTERNAL COMBUSTION ENGINE TECHNICAL FIELD OF THE INVENTION The invention is concerned to a accumulator-regenerative internal combustion engine, which finds application in operating vehicles and immobile machines and facilities, used for various kinds of business activities as well as for high/middle-pressured fluid compressors.

BACKGROUND OF THE INVENTION The 4-stroke Piston Internal Combustion Engine in petrol or diesel versions, consisting of cylinder block with formed within it operation cylinders, wherein a piston is mounted in everyone of them, connected by a rocker to a crankshaft whereto a distributive cam shaft is connected by means of a 2: 1 gear ratio- mechanical transmission, is well-known. The cams are plug-connected to inlet and exhaust valves mounted within inlet and exhaust holes formed for everyone of the operative cylinders into a cylinder head immobile joined to the cylinder block wherein a hole is made for mounting both a sparking plug or a fuel- injection nozzle. The crankshaft is connected by a operated vehicle transmission by a connector, which has an arresting system controlled by a brake-pedal to reduce motion velocity of the transport vehicle and an accelerator to support or increase motion velocity of the transport machine.

The internal combustion engine shortcomings are such that when a reverse rotation moment is delivered, from the transmission drive of the operated transport machine to the engine's crankshaft, for instance, in motion of the transport machine in downward slope with no fuel feeding, to the operation cylinders, the engine operates as power consumer with negative efficiency since the consumed power delivered by the operated transport machine's inertial mass owing to the thermodynamic losses in the operation room of the operation cylinders is converted in unusable heat, detached to the ambience. The "positive"effect in consumption of this power is expressed as arresting action upon the motion velocity of the transport machine, which action is scanty for its

efficient deceleration. It is imposed intensive using the brake system, which becomes a consumer of the kinetic and potential energy stored up to here by the internal combustion engine as inertial mass of the transport machine, which is conversed into unusable heat detached in ambience. Another shortcoming of the internal combustion engine is in that a relative great part (25-55%) of the thermal energy produced in the combustion process is not used in yield but it is taken away in the ambience along with the exhausted gases. Moreover, hot exhausted gases are remained in the operation room of the operation cylinders following the cleaning process because of that intensive heat exchanging is carried out by them and by walls enclosing the operation room which have relative high temperature resulted by the combustion, expansion and cleaning in relation to the atmospheric air or the fuel/air mixture incoming in the loading process by which the conditions of the progress of the loading, comression and combustion processes are worsened. As well as in operation in closed rooms for a short time even, a progressive increasing concentration of exhausted gases wasted in the closed room which progressive decreases volume of the atmospheric air in that rooms, which is dangerously for health of human in these closed rooms. Other adverse circumstances are availability of an additional power unit for initial starting engine and a air compressor to feed the brake system of the operated by it transport machine as well as the necessity the engine to operate in idle running for short idle times as well as in inertial motion of the transport machine. Owing to all mentioned here shortcomings the fuel consumption, the thermal and toxic ambient contamination as well as the wear of the transport machine's engine per unit of traveled run are considerably increased (1."Technical Thermodynamics"] (Tehnicheska Termodinamika), Tehnika, Sofia, 1970, pp. 252-253, 259-260,278-279,287-288, and 296-298).

A gas-distributive assembly of 4-stroke internal combustion engine wherein the distributive shaft is on bearings in carrier suspended on joint axle whereto data sensors accounting its angular position (bearing/azimuth and elevation) linked to a microprocessor for executive mechanism control connected to a carrier arm

A shortcoming of this gas-distributive mechanism is that it provides conditions for passing thermodynamic processes within the operation cylinders, typical for internal combustion engine only (2. BG Patent 45337, Class A : F 01 L1/34) A Piston hot-air machine is well-known, whose structure is identical to the internal combustion engine one's with that distinction that the exhaust holes of a part of its operation cylinders termed as a"compressor"are connected to the inlet holes of the second part of the operation cylinders, termed as"pneumatic engine"by means of fitting pipelines jointed in serial by means of a heat exchanger plugged-in to external (outer) heater. The exhaust holes of the operation cylinders of the"pneumatic engine"are connected to inlet holes of the operation cylinders of the"compressor"by means of fitting pipelines jointed in serial to a heat exchanger coupled to outer cooler.

The shortcomings of the hot-air machine are that a great part of the benefit work of the"pneumatic engine"is spent to operate the"compressor"as well as it is need by outer thermal source fo heating the compressed air which passes through the heat exchanger connected to that outer thermal source [3].

SUMMARY OF THE INVENTION The aim of the invention is to create a restore-regenerative internal combustion engine, which to be reshaped classical internal combustion engine with inner or outer mix making in such manner that it to work not only as internal combustion engine as well as to converse and store the surplus kinetic energy accumulated first into the internal mass of the powered vehicle in during its motion as well as for conversion of a part of the thermal energy containing into exhausted gases in its working as internal combustion engine into potential energy could be regenerate into rotation momentum delivered to the transmission drive of the powered vehicle.

In according to the invention this problem is solved by the storage-regenerative internal combustion engine composed of a cylinder block, operation cylinders provided with pistons, reels, crankshaft connected to the transmission shaft of the powered vehicle provided with a brake system, brake-pedal, accelerator

pedal, a chain-driven toothed gear provided with a central cogwheel of a bearing on a central axle, a cylinder head provided with a hole for fuel-a jetting nozzle or a sparking plug, inlet and exhaust holes provided with valves in them and connected to the rockers with formed on them plug stages, a data sensor and a servo-drive, connected to the carrier and plugged-in to a microprocessor. Furthermore, a second distributive shaft provided with cams is on bearings in the carrier as each of the cams is located on a common plain along with the rocker's plug stage and along with the distributive shaft's cam. A single carrier connected to a single servo-driver is suspended on each of the operation cylinders. A common central shaft on bearings upon the central axle and plugged-in to the chain toothed gear by means of the central chain-driven cogwheel coupled to it, passes cross the single carriers. The distributive shafts are joined to the crankshaft in 2: 1 gear ratio; the crankshaft is joined to the second distributive shafts in 1 : 1 gear ratios. In the cylinder head, a feeding and a compressing holes are formed, which as well as the feed hole by means of a re- distributor with initial switchers, each of them is provided with a single"i-m" servo-driver, are connected in serial to"n"numbers of cooling tank's chambers and to a heating tank. Within the cooling tank, a heat exchanger is mounted, it is always plugged-in to an outer cooler, but in the heating tank a heat exchange is mounted which by means of the re-distributor with final switchers, each of them with single i-m servo driver, is selectively connected to the exhaust hole for the operation room of t he operation cylinders. An one-way barrage-feed valve is mounted in the feed hole of the operation cylinders which is composed of a feeding valve provided with valve a washer pressed by a spring to the pass holes made in a cone-formed cup, and by a barrage valve provided with a spindle pressed by a valve spring and plug-in connected to a cam, to a valve bed, the said cam is formed upon pressing shaft whose second cam is plug-in connected to a spindle of the barrage valve adjoining to an one-way barrage-compressing valve with compressing valve composed of a valve washer pressed by a spring to the said pass holes, made in a cone-formed cup which is mounted within the compress hole.

Furthermore, to the central axle of the bearing grounds for each of the operation cylinders a carrier is articulately suspended on bearings in it an axle-moved distributive shaft with formed by 1 piece first feeding cam located next to rocker's plug stage, adjoining to the feeding hole's valve, and by 1 piece exhaust cam, located near to the rocker's plug stage, adjoining to the exhaust hole's valve. Close to them but in other plains by two pieces are formed by 2 pieces of feed cams transposed each to other on 180° and by 2 pieces of exhaust cam each to other on 180° too. On the axle-movable distributive shaft, are made grooves axle-movable in groove channels made in the central hole of a big central cogwheel with bearings in supports formed in the carrier whereon an axle- movable sleeve with a fork put in a diametrical channel made in the axle- movable distributive shaft and connected to an'i-m'the servo-driver. On a second central axle per each of the operative cylinders an additional carrier is articulately suspended which is connected to an'i-m'servo-driver and wherein an additional distributive shaft with formed two pieces of feeding cams locate in 90° each to other and positioned to the plug stage formed on a rocker plug- connected to the barrage valve's spindle, is on bearings in it. On an axle in the additional carrier are on bearings a pressing roller positioned against the pushing out cams, and a pressing roller positioned against feeding cams of the additional distributive shaft whereto a cogwheel is coupled which is in clutching with the central cogwheel is positioned on second central shaft on bearings on the second central axle and it is plugged-in by the chain-driven cogwheel and driving chain to the chain tooth gear of the crankshaft with 4: 1 gear ratio, respectively, to the additional and to the axle-movable distributive shafts.' In other type of version implementation of the engine, axle-movable distributive shaft is on bearings on the additional carrier whereon two pieces of feeding cams and two pieces of pushing out cams are formed, and near to the feeding cams but in another plain a third feeding cam is formed.

In same time, to the central shaft are on loosely bearings first and second drawing wheel, as in each of them lockable centering beds located on different distances from the rotation axle wherein locking pins coupled to two-side micro

plungers mounted in little servo cylinders each of them having by two operation rooms and connected by channels made in the central shaft with transition rooms generated between the central shaft and mounted to a it fixed transferring head which are selectively plugged-in by three-way tap provided with'i-m'servo- driver to the heating tank or the atmosphere air.

Furthermore, the chambers of the cooling tank by the re-distributor are connected to the inlet and compressing holes of a compressor.

The advantages of the Storage-Regenerative Internal Combustion Engine (SRICE) are that it matches in itself a piston internal combustion engine, which in several cases operates both and as an middle/high pressure air-compressor and as a pneumatic engine too, as well as some its versions it carries-out a combined operation cycle, which is consist of consecutively carrying-out 1 piece of full operation cycle of 4-stroke internal combustion engine and 2 pieces of operation cycles of pneumatic engine as well a part of the thermal energy transmitted by the operation gases to the walls, which enclose the operation room of the operation cylinder duration of the combustion, expansion and cleaning processes wherein it is unevenly distributed along their cross-section as well as the thermal energy containing within the exhausted gases remained within the operation room of the operation cylinders behind the cleaning process, is utilized as benefits work as it is added to the compressed air in-taking into the operation room in the expansion from the two operation cycles of pneumatic engine as thereby the conditions of the loading, compression, and combustion processes are improved for the 4-stroke operation cycle from the next combined operation cycle. There is a reduced fuel consumption and hereby and reduced volume of exhausted gases wasted in the atmosphere per unit of completed work since it utilizes as benefits work the surplus kinetic energy accumulated within the inertial mass of the operated transport machine duration its motion as well the thermal energy containing into the exhausted gases wasted in the atmosphere duration its operation as 4-stroke internal combustion engine, as well as that it possesses self-starting functions and it is not need by detached power source for initial starting. The necessity of detached compressor charging

high/low-powered consumers of compressed air positioned on or out of the powered vehicle. It performs the base brake functions to decelerate the powered vehicle or stop it. There is not idle running mode as well as it possesses neutral running wherein in several cases of rotation momentum delivering from the transmission drive of the powered vehicle to the crankshaft in the operation cylinders no thermodynamic processes are performed thereby despite the pistons strokes mechanical work neither is generated nor is consumed. It provides some running of the powered vehicle when the fuel tank is empty as well as in cases of serious troubles in the feeding or ignition systems of the 4-stroke engine and that for a several period of time it can operate in closed rooms with no contamination of the ambient air wit exhausted gases.

BRIEF DESCRIPTION OF THE DRAWINGS The invention is explained in details by means of an illustrative implemented Storage-Regenerative Internal Combustion Engine (SRICE), which is shown on the figures as follows: Figure 1 : Assembly Diagram of 3-cylinder SRICE ; one of its operation cylinders is shown only.

Figure 2: Schematic Section of one of SRICE's Operational Cylinders and of part of its Cylinder head done across the axle of the Crankshaft.

Figure 3 : Schematic Section of the Cylinder head and a part of the Operation cylinder is shown, it is done across the inlet valve's spindle crosswise of the Central shaft.

Figure 4 : Schematic section of the Carrier along with bearings into it distributive and second distributive shafts done crosswise the axle of the Central shaft.

Figure 5 : Section of the Cylinder Head done across the barrage-feeding valve.

Figure 6: Section of the Cylinder head done across the barrage-compressing valve Figure 7 : Section of the Carrier along with bearing into it axle-movable distributive shaft done across the Central shaft's axle.

Figure 8: Schematic Section of the Additional Carrier along with the bearing into it an additional distributive shaft and pressing rollers done across the Second Central shaft's axle.

Figure 9: Schematic Section of the Additional Carrier done crosswise of the Second Central shaft and across the barrage-compressing valve.

Figure 10 : Axonometric View of the Additional Axle-Movable Distributive Shaft.

Figure 11: Schematic Section of the Central drawing wheels, Servo-driver cylinders and the Transferring Head.

EXEMPLARY EMBODIMENTS OF THE INVENTION As it is shown on the Figures from 1. to 11, the Storage-Regenerative Internal Combustion Engine (SRICE) is consist of a reconstructed piston 4-stroke internal combustion engine composed of : a cylinder block 1, operation cylinders 11 with operation room 12, pistons 12, clutches 14, a crankshaft 15 connected by connector 19 to the shaft of a transmission drive 18 of the powered vehicle along a brake system 183, brake-pedal 182, accelerator (-pedal) 181. Towards the cylinder block I is joined a cylinder head 2 along with a hole designed for both a fuel-jetting nozzle or a sparking plug 29, along with inlet 22 and exhaust 25 holes, inlet 22 and exhaust 26 valves, rockers 23,27 along with formed on them plug stages 24,28 in form of part of cylindrical surface along with a central axle 300, whereon a carrier is articulately suspended whereto a'i-m'servo-drive and'i'data sensor are connected in serial and plugged to a microprocessor 30.

On the carrier a cam distributive shaft is bearing, its cams are plug-connected to the plug stages 24,28. On the Central axle 300 upon bearing supports 20 per each of the operation cylinders 11 by one carrier 3 along with the adjoining to it 'i-m3'servo-drive and'i'data sensor connected to a microprocessor 30, are articulately suspended. In each carrier 3 are bearing by one distributive shaft 4 along with cams 44,48 located to the relevant plug stages 24,28 and by one second distributive shaft 5 along with cams 54,58 located, respectively, in a common plain along with the cams 44,48 in the same plain of the distributive

shafts 4. On each of the distributive shafts 4 is coupled by one large drawing cogwheel 41 which is clutched to one from the first central cogwheel 40 coupled to the central shaft 6 bearing on the central axle 300 whereon are articulately suspended and the carriers 3. On the each of the second distributive shafts 5 is coupled by one drawing cogwheel 51 which is clutched to one of the second central cogwheels 50 coupled to the central shaft 6 too whereto is coupled and the central chain-driven cogwheel 60, which by means of driving chain 17 is clutched to chain cogwheel 16 located on the crankshaft 15. The end gear ratios from the crankshaft 15 to the distributive shafts 4 is 2: 2, and to the second distributive shafts 5 is 1 : 1.

Towards to the spindle of each of the inlet valves 22 is located balancing micro- piston 221 along with sealing ringlets located in the micro-cylinder 223 with operation room 21 formed in the cylinder head2, wherein per each of the operation cylinders 11 are formed else inlet hole 7 and compress hole 8. In the inlet hole 7 is mounted one-way barrage-inlet hole 70, and into compress hole 8 is mounted one-way barrage-feeding 70 and barrage-compress 80 valves. Each of the one-way barrage-compress 70 and barrage-feeding valves 80 is consists of valve bed 71,81 coupled by means of cone-formed cup 72,78 along with carrier 73,83. In the cone-formed cup 72,82 are made pass holes 74,84 whereto by means of spring 75,85 is pressed valve washing 76,86. In the valve bed 71,81 is located barrage valve 77,87 along with spindle 78,88 centered to the guide 73,83 whereto is coupled valve spring 79,89. The spindle 78,88 is plug connected to cam781,782, located near to its front part and formed upon pressing shaft 780 whereto are connected'i'data sensor and'i-m'servo-drive 780.

The feed hole 21, the inlet hole 7, the compress hole 8, and exhaust hole 25 by means of re-distributor 94 and connecting pipeline are plugged to storage- regenerative system 9, composed of cooling tank 91 consisting of located one in other'n'numbers chambers 911,912,913... up to'n', wherein is located heat- exchanger 910 plugged to outer cooler 93 and they are mutual connected by one-way valves 901,902,903. The last chamber 913, located on the interior of the rest by means of connecting pipeline and one-way demarcating valve 909 is

connected to heating tank 92 wherein is located heat exchanger 920. By means of initial switchers 94 L, located to the re-distributor 94 per each of the operation cylinders 1 l., chambers 911, 912, 913 of the cooling tank 91 and heating tank 92 are selectively connected to the feed hole 21, to inlet hole 7 and to compress hole 8, adjoining to the separate operation cylinders 11, and their exhaust holes 25 by means of end switchers 942 located on re-distributor 94 are selectively connected to the atmosphere 95 through the heat-exchanger 920 of the heating tank 92 or directly. Each of the initial 941 and end switchers is connected to the servo-drives'i-m'941 and'i-m'942 for changing their operation positions.

Towards heating tank 92 by means of connecting pipeline is connected tap along with a valve-reducer 97, and to the heat exchanger 920 is mounted an additional thermal source 96. In the chambers 91 l, 912,913 of the cooler tank 91 and into heating tank 92 are located data sensors'i'.

An version realization is possible wherein in the carrier 33 articulately suspended on the central axle 300 is bearing axle-movable distributive shaft 400 along with grooves 401 made in its one end, which are axle-movable and located into groove channels 402 made into the central hole of a large cogwheel 403 with bearings on supports 404 formed in the carrier 33. Over the axle-movable distributive shaft 400 near to the plug stage 24 of the rocker 23 is located one piece first feeding cam 444, near to it on second plain are located two pieces second feeding cams 454, phase-shift each other on 180°. In the axle-movable distributive shaft 400 is made outer diametric channel 405 wherein with windage is located a fork 406, mounted by means of a washer 407 axle-fixed over carrier 33 and connected to servo-drive'i-m'406 for axle shift. Over axle- movable distributive shaft 400 near to the plug stage 28 of the rocker 27 is located one piece of first exhaust cam 448, and near to it on second plain are located two pieces of second exhaust cams 458 phase-shift each other on 180°.

On second central axle 800 is articulately suspended additional carrier 333 connected to servo-drive'i-m'333 and to data sensor i, as in the additional carrier 333 is bearing an additional distributive shaft 700 along with formed on it two pieces of inlet cams 701,702 shift each other on 90°, and two pieces

pushing out cams 801,802 shift each other on 90°, and in relation to feeding cams 701, 702-on 45°. The inlet cams 701,702 are located near to plug stage 703 formed on rocker 704 and plug connected to the spindle 78 of the barrage valve 77, and the pushing out cams 801,802 are located near to plug stage 803 formed on the rocker 804 and plug connected to the spindle 88 of the barrage valve 87. Towards the additional carrier 333 of axle 708, located in parallel of axle of the additional distributive shaft 700 are bearings pressing rollers 705,805 as the pressing roller 705 is located on one plain with inlet cams 701, 702, and pressing roller 805 is located on one plain with the pushing out cams 801,802.

On the additional distributive shaft 700 is placed drawing cogwheel 706, which is clutched to the central cogwheel 707 located on second central shaft 806 bearing on second central axle 800, whereon is articulately suspended the additional carrier 333. Towards the second central shaft 806 is located the chain cogwheel 807, which by driving chain 808 is clutched to second central chain cogwheel 809 located on the central shaft 6 as in this version realization the end gear ratios of the tooth gears from the crankshaft 15 to the axle-movable distributive shaft 400 and the additional distributive shaft 700 are 4 : 1.

It is possible within the additional carrier 33 to be bearing the axle-movable shaft 900 whereon are formed both the two pieces inlet cams 701,702 and the two pieces pushing out cams 801, 802 as near to the inlet cams 701,702 but in another parallel plain is formed third feeding cam 944. Towards axle-movable distributive shaft is connected servo drive for axle shift, which are not shown on the figures.

In another version realization, on the central shaft 6 is possible to be free bearing radial and axial first 61 and second 62 central drawing wheels as in each of them are formed barrage-centering beds 611,612; 621,622, located at different ranges from the rotation axle wherein are selectively placed locking pins 511,512 coupled to the micro-plungers 510, 520 mounted in executive micro cylinders 500 each of them with by two operation rooms 501,502, which are connected by channels 503,504 made into the central shaft 6 with transition rooms 505,506 formed between the central shaft 6 and mounted to it fixed transferring head 507

connected by a three-way valve 508 to the servoidrive . i-m'508, selectively to the heating tank 92 or to the atmosphere 95. The first central drawing wheel 61 by driving chain 171 is clutched with gear ratio 1 : 1 to guiding wheel 161, coupled to the crankshaft 15 whereto is coupled and second driving wheel, which by driving chain 172 is clutched with gear ratio 2 : 1 to the second central drawing wheel 62. <BR> <BR> <P>It is possible the cooling tank 91 by the re-distributor 94 to be connected to<BR> feeding and to compress holes, are (not shown on the figures) of a air/gas compressor.

OPERATOR OF THE DEVICE The work position of the carriers 3,33 and the additional carrier 333 of initial 941 and end 942 switchers of the pressing shaft 780, of axle-movable distributive shafts 40Q, 900 and of the three-way tap 508 are altered by their adjoining servo drives'i-m'on commands of the microprocessor 30 issued to the relevant servo-drives in depending on data received by data sensors for the particular performance situation, specified by : the extent of accelerator 181 and brake 182 pedals shifts, the extent of compressed air charging of cooling 91 and heating 92 tanks as well as by the temperature loading of walls enclosing the operation room 12.

In non-pressed accelerator pedal 181 and brake pedal 182, the carriers 3 are articulately turned around the central axle 300 so that the distributive shafts 4 and the second distributive shafts 5 are equal distanced by the plug stages 24,28 of the rockers 23,27 whereupon the cams 44,48,54,58 are not plugged to the plug stages 24,28. In result of that, the feed holes 21 and exhaust holes 25 are always closed by the feed valve 22 and exhaust valve 26. The pressing shafts 780 are turned around its axles, so that the cams 781,782 press the spindles 78,88 of the barrage valves 77,87 deforming the springs 79,89 and opening always the valve bed 71,81 holes. The initial switchers 941 are located in neutral positions whereupon the inlet holes 7 and compress holes 8 of all the operation cylinders 11 are connected one other to the common room, which is not shown

on the figures. When the crankshaft 15 is turned by an external force in the operation cylinders 11 wherein the pistons 13 are moved from UDP (upper dead point) to BDP (bottom dead point) a down pressure is produced, but the operation cylinders 11 wherein the pistons 13 are moved from BDP to UDP an over pressure is produced. The produced down pressure and over pressure are mutual balanced by the common room and passing holes 74,84, opened and closed by the relevant valve washers 76,86 under impact of the their springs 75,85 and under impact of the force generated by pressure difference under and over them. Thereby, transfer of the gases from the operation cylinders 11 is done wherein the pistons 13 are in move from BDP to UDP into the operation cylinders 1 l hereby with the operation rooms 12 a neutral cycle is performed at which mechanical energy neither is generated nor is consumed with the exception of that one, which is needed for surmounting the friction force and the hydraulic losses. In this case, the vehicle moves by inertia as it consumes the kinetic energy stored up to here into its inertial mass for surmounting resistant forces generated in its motion and the crankshaft 15 rotation.

At pressing the brake pedal 82, depending on the extent of its shift, the initial switchers 941 of one, two or more operation cylinders 11 are shifted as its inlet hole 7 is connected to the atmosphere 95, and their compress hole 8-to the first chamber 911. At stroke of pistons 13 from UDP to BDP, air sucks in from the atmosphere, which surrounds the force of the spring 75 and through the opened by the valve washer 76 passing holes 74 it intakes into the operation room 12, which air at the opposite piston 13 stroke from BDP to UDP it is compressed, surmounting the spring 85 force and through opened by the valve washer 86 passing holes 84 is supercharging into the chamber 911 of the cooling tank 91.

The compressed air supercharge into the chamber 911 continues up to reaching utmost permissible difference between the initial and end pressure of the compressed air known from the compressed air compressor, at which the initial switchers 941 of one, two or more operation cylinders 11 connect their inlet hole 7 to the chamber 911, and their supercharging hole 8-to the chamber 912, hereby at piston 13 stroke from UDP to BDP in the operation room 12 enters

compressed air from the chamber 911, which at the piston 13 stroke from BDP to UDP is compressed for second time and it is supercharged to the chamber 912, which supercharging continues up to reaching the utmost permissible difference between the initial and end pressure. At reaching the pointed difference the initial switchers 941 of one, two or more operation cylinders 11 connects their inlet holes 7 to the chamber 912, and their supercharging holes 8 -to the chamber 913, wherewith at piston 13 stroke from UDP to BDP in the operation room 12 intakes compressed air from the chamber 912, which air at the piston 13 stroke from BDP to UDP is compressed for third time and it is supercharged into the chamber 913, from where through the one-way demarcating valve 909 passes into the heating tank 92. Depending on the extent of shifting brake-pedal 182, a part of the operation cylinders 11 remain to work in a neutral cycle, and the rest two, three or more remain to work as compressed air compressor, compressing repeated one and the same volume of air up to higher values of its pressure, wherewith the surplus kinetic energy stored up to here into the inertial mass of the powered vehicle is converted into potential energy in the form of compressed air stored in the cooling tank 91 and the heating tank 92 as simultaneously by that it renders efficient braking impact for supporting or decelerating the vehicle motion velocity. At extremely shifting of the brake-pedal 182, the vehicle brake system 183 is casually actuated.

At releasing the brake-pedal 182 by pressure and its return in initial position by the microprocessor commands to the relevant'i-m'servo-drives, the operation cylinders automatically proceed to work in neutral cycle.

At insufficient charging of the cooling tank 91 and the heating tank 92 with compressed air and at influence on the accelerator pedal 181 depending on the extent of it shifting, the carrier 3 of one, two or more operation cylinders 11 are articulately turned around the central axle 300, so that their distributive shafts 4 are located near to the plug stages 28. In turning of the distributive shafts 4, cams 44,48 control the opening and closing inlet holes 21 and exhaust holes 25 of the operation room 12 in sequence and cyclic recurrence fully identical with ones of the known classical 4-stroke internal combustion engine. The operating

cycle of the loading, compression, combustion, expansion and cleaning processes is realized in four strokes of the piston 13, reckoned from UDP to BDP and vice versa. The exhaust hole 25 by the end switcher 942 is connected to atmosphere 95 through the heat exchanger 920, by which the exhausted gases give a part of its thermal energy to the compressed air located into the heating tank 92 wherewith they increase its temperature and pressure, and wherewith and its stored potential energy. At reaching of several pressures into the heating tank 92, the fuel feeding by the fuel-jetting nozzle to one, two or more operation cylinders 11 is stopped. Simultaneously with that, their carriers 3 are turned around the central axle 300 so that the second distributive shafts 5 to be located near to the plug stages 24,28, whereupon the cams 54 get into contact with the plug stages 24, and the cams 58 get into contact with the plug stages 28.

Simultaneously with that, their feeding holes 21 by the initial switchers 941 are connected to heating tank 92, and the exhaust holes 25 by the end switchers 942 are directly connected to atmosphere 95. In rotation of the second distributive shafts 5 their cams 54,58 control the opening and closing of the feeding holes 21 and exhaust holes 25 of the operation room 12 in sequence and cyclic recurrence fully identical with ones of the known pneumatic engine. The operating cycle along the expansion and exhausting processes is realized for two strokes of the piston 13, reckoned from UDP to BDP and vice versa. The pressure power of the compressed air located into the feeding hole, acting towards in direction of opening feeding valve 22 is balanced by the force generated by the same this pressure acting on the micro plunger 221 in direction of closing feeding valve 22. At the operating cycle of the pneumatic engine is regenerated the stored potential energy in the form of compressed or hot compressed air. At end shift of the accelerator pedal 181 and full charging of the cooling tank 91 with compressed air, the initial switchers 941 of the operation cylinders 11 operating as 4-stroke internal combustion engine connect their feeding holes 21 to the chamber 913 of the cooling tank 91 wherewith forced loading of the operation room 12 with compressed air is realized.

At releasing of the accelerator pedal 181 in initial position, all the operation cylinders 11 automatically transit to operating in neutral cycle.

In version realization with axle-movable distributive shafts 400, on bearings in the carriers 33, the plug stages 24,28 of the rockers 23,27 get into contact, respectively, with the first feeding cam 444 and with the first exhaust cam 448 whereupon the relevant operation cylinder 11 operates as an internal combustion engine or get selectively in contact, respectively, with the second feeding cams 454 and with second exhaust cams 458 whereupon the relevant operation cylinder 11 operates as a pneumatic engine. The axle shifting axle-movable distributive shafts 400 is accomplish in a moment when their carriers 33 are articulately turned about the central axle 300 so that the cams 444,448,454,458 do not get in contact with the plug stages 24,28.

In version realization with axle-movable distributive shafts 400 and the additional distributive shaft 700, the operation cylinders 11 besides by mentioned above operation cycles, operate else and by a combined operation cycle composed of one operation cycle of 4-stroke internal combustion engine and two consequent operation cycles of pneumatic engine. For accomplishment of the combined operation cycle the plug stages 24,28 of the rockers 23,27 to contact, respectively, with the first feeding cam 444 and first exhaust cam 448 of the axle-movable distributive shaft 400, the plug stage 703 of the rocker 704 to contact with the feeding cams 701,702 of the additional distributive shaft 700, whereon the pushing out cams 801,802 to contact with the plug stage 803 of the rocker 804, the feeding hole 7 by the initial switcher 9421 to be connected to the heating tank 92, and the supercharging hole 8 by the end switchers 942 to be directly connected to atmosphere 95. The realization of the combined operation cycle passes off for four strokes of the crankshaft 15, eight strokes of the piston 13 and 1 revolution of the axle-movable distributive shaft 400 and of additional distributive shaft 700 in the follow order: in first four piston 13 strokes the feeding hole 7 and supercharging hole 8 are always closed by the barrage valves 77,87, in first piston 13 stroke from UDP to BDP the feeding hole is opened under influence of first feeding cam444 on the feeding valve 22 by the pressure

rendered on the plug stage 24 of the rocker 23 whereupon the loading process is implemented, in the second and third piston 13 strokes the compression, combustion and expansion are implemented, in the four piston 13 stroke the exhaust hole 25 is opened under influence of first exhaust cam 448 on the exhaust valve by the pressure rendered on the plug stage 28 whereupon the cleaning process whereby the composed 4-stroke operation cycle of internal combustion engine is completed. In the remained four strokes of piston 13, the feeding hole 21 and exhaust hole 25 are always closed. In the fifth stroke of the piston 13 from UDP to BDP the feeding hole 7 is opened by the barrage valve 77 under influence of the feeding cam 701, rendering pressure on the plug stage 703 of the rocker 704, whereupon from the heating tank 92 into the operation room 12 intakes compressed air, which renders pressure on piston 13 frontage as moved it to the BDP generating benefits rotating momentum applied by the clutch 14 to the crankshaft 15. In the opposite stroke of piston 13 from BDP to UDP, the supercharging hole 8 is opened by the barrage valve 87 under influence of the pushing out cam 801 rendering pressure on the plug stage 803 of rocker 804 whereupon the waste air from the operation room 12 is directly pushed out into atmosphere and hereby the first composed operation cycle of pneumatic engine is completed. In the next two strokes of piston 13 an identical second composed operation cycle of pneumatic engine is accomplished, at which the feeding hole 7 and supercharging hole 8 are opened by the barrage- valves 77,78 under influence of the feeding cam 702 and the pushing out cam 802 rendering pressure, respectively, on the plug stage 703 and on plug stage 803. After the process of push out within the operation room 12 completes, a new combined cycle starts. After the composed operation cycle of 4-stroke internal combustion engine is completed, the residual waste gases remaining within the operation room 12 and enclosing it walls have relative high temperature, which renders positive effect in the next first composed operation cycle of pneumatic engine wherewith the relative heat transfer from the operation room to the atmosphere is reduced, the operation room 12 is fully cleaned from the remaining wasting and the enclosing walls temperature is

lowered the second composed operation cycle of pneumatic engine, whereby a positive effect on the loading, compressing and combustion processes of the next composed operation cycle of 4-stroke internal combustion engine is rendered. In version implementation of the central shaft 6 along with the freely bearing upon it central drawing wheels 61,62 and formed within them barrage- centering beds 611,612; 621,622 a possibility is provided for two-stage gear ratio change from the crankshaft 15 to the central shaft 6 too, and hereby to the distributive shafts on bearings on the carrier 3,33 and the additional carrier 333 whereby the functional capacity of the operation cylinders is increased for operation with various kinds of operation cycles. The two-stage gear ratio change from the crankshaft 15 to the central shaft 6 is accomplished by varying operation position (operational repositioning) of the three-way tap 508 by the'i- m'servo drive 508 by commands of the microprocessor 30 preceded by overtaking commands to the'i-m'3,'i-m'33, and Gi-m'333 service drives, which put the relevant carriers in position whereupon the cams of the adjoining them distributive shafts are not in operation contact. It is necessity the three-way tap 508 to be placed in operation position for locking the central drawing wheel 62 to the central shaft 6 whereupon compressed air is passed from the heating tank 92 through channel within the transferring head 507, the transitional room 505, the channels 503 within the operation room 501 of the servo-driving micro- cylinders 500, where the micro-plungers 510,520 to the central drawing wheel 62, the locking pins 511, 512 get into sliding contact to the its frontage upon concentric catenaries with central angle from 0° to 360° depending on the coincidence moment of the locking pin 511 axle on the locking-centering bed 621, and the axle of the locking pin 512 is coincided to the lock-centering bed 622 axle, whereupon the locking pins 511,512 get in the relevant lock-centering beds 621,622, whereby they lock the central drawing wheel to the central shaft 6 in solely possible position, which provides constructive defined synchronization between the pistons 13 motion and opening of the feeding hole 21, inlet hole 7, supercharging hole 8, and the exhaust hole 25 of the operation room 12. The lock of the central drawing wheel 61 to the central shaft 6 is by analogy and it is realized by feed of compressed air to the operation rooms 502 of the servo driving micro cylinders 500, preceded by connection of the operation rooms 501 to atmosphere 95 by the three-way tap 508.