RU2215879C2 - Piston machine (versions) - Google Patents

Abstract

FIELD: mechanical engineering; internal combustion engines. SUBSTANCE: proposed piston machine contains at least two cylinders with pistons moving inside cylinders and rotary cylindrical spools connected with cylinders by bypass channels and arranged in intake and exhaust chambers. Intake chamber is located over one cylinder, and exhaust chamber, over other cylinder, each chamber operates to two cylinders. According to invention proposed piston machine contains minimum two adjacent operating cylinders with working spaces which accommodate pistons each coupled with its crank. Spools coupled with pistons move in intake and exhaust chambers. Intake and exhaust ports are made in operating cylinders over pistons. When the later are in top dead center, said ports are connected by bypass channels with ports of intake and exhaust chambers. Spools are coupled with pistons by means of rods. Chambers are installed over pistons through separating partitions. EFFECT: improved efficienc6y in operation. 8 cl, 15 dwg

Description

 The invention relates to mechanical engineering, in particular to the design of reciprocating two-stroke and four-stroke internal combustion engines, as well as to the design of reciprocating compressors and pumps, which have a piston movement mechanism and a working cylinder with inlet and outlet windows.

 As a group of inventions, several independent piston engine versions are proposed, which can be used for various purposes while maintaining the main distinguishing features. All variants of the piston machine have one look and provide a similar technical result, because provide gas compression or pumping a liquid medium using the translational movement of the pistons and the operation of the distribution mechanism.

 As the closest prototype for a piston machine having a cylinder, a piston, inlet and outlet windows, and also a device for closing the windows, a piston machine having the same limiting features can be adopted. Such a piston machine can include four-stroke and two-stroke internal combustion engines, as well as compressors for compressing and suctioning gases (vacuum compressors) and piston pumps for pumping liquid media.

 All of the known variants of the piston engine listed above have a complex gas distribution mechanism with a number of disadvantages that reduce the technical and economic performance of the piston engine. So, for example, in a four-stroke engine, the gas distribution mechanism includes forced-lift valves and a cam shaft. The lifting valves and the camshaft have unbalanced inertial masses that limit the rotation speed of the motor shaft and prevent it from developing its maximum possible power. The presence of valve plates overlapping the windows does not ensure their full opening and increases the resistance of the gas path. To reduce the resistance of the gas path, sometimes several lift valves are used for one cylinder, but this greatly complicates the design of the engine.

 A gas distribution mechanism having a camshaft, valves, pushers, is subject to rapid wear, has a low mechanical efficiency and an increased noise level. As the camshafts and cam followers wear out, periodic clearance adjustment is required during operation.

 In reciprocating compressors and pumps, self-acting lifting valves are used as a distribution mechanism, the shut-off elements of which also have unbalanced inertial masses. Therefore, self-acting valves have low reliability and do not allow to increase the speed of rotation of the piston machine.

 In two-stroke internal combustion engines, windows made on the cylinder wall, which are overlapped by a piston, are used as a distribution mechanism. This arrangement of windows entails the need to increase the length of the cylinders and pistons. If the length of the cylinders and pistons is short, there is a chance that the oil will escape from the crankcase into the exhaust ports and fuel will enter the crankcase through the intake ports. In addition, for this reason, it is necessary to place additional piston rings on the bottom of the piston skirt.

 The objective of the invention is to increase the technical and economic indicators of a piston machine by simplifying and increasing the reliability of the distribution mechanism of machines that compress gas or pump liquid.

 As the closest prototype, we can take the design of the piston machine used as an engine-compressor, which is described in the book [2].

 A disadvantage of the known machine is the low efficiency of its work.

 The technical result for all options is to increase efficiency.

 The task in part of the first embodiment is achieved by the fact that the piston machine, for example, as a two-stroke or four-stroke internal combustion engine, a compressor for compressing or sucking gas or a pump for pumping a liquid medium containing cylinders with cavities in which the pistons, the intake chamber and the chamber move of the outlet, in which the cylindrical spools connected with the motor shaft rotate, and the inlet and outlet windows connected by the bypass channels to the intake and exhaust chambers, according to the invention, contains at least two cylinders, the inlet chamber is located above one cylinder, and the exhaust chamber is above the other, with each chamber working on two cylinders.

 The task is also achieved by the fact that the cavity of the cylinders can be interconnected using a channel with the formation of a common combustion chamber for two cylinders, and the pistons move in one direction, while one cylinder has inlet windows and the other cylinder has outlet windows, or the cylinders operate independently of each other, the pistons of the cylinders counter-move and work in antiphase, two spools are placed in the intake and exhaust chambers, and each cylinder has an inlet and an outlet window.

 The task in part of the second option is achieved by the fact that in a piston machine containing at least two adjacent working cylinders with working cavities in which pistons are moved, each connected with its crank, intake chambers and exhaust chambers in which spools connected with pistons are moved , inlet and outlet windows made in the working cylinders above the pistons at their position at top dead center and connected bypass channels with the windows of the intake chamber and exhaust chamber, according to the invention, anes to the pistons by means of rods, a camera installed above the working piston through the separating partition.

 The task is also achieved by the fact that the working cavities can be interconnected using a channel with the formation of a common combustion chamber for two working cylinders, the pistons move in one direction, while one cylinder has inlet windows and the other cylinder has outlet windows, or the cylinders are independent, the working pistons counter-move and work in antiphase, with each cylinder having inlet and outlet windows.

 The task is also achieved by the fact that the spools can be made of rectangular cross-section.

 The task in part of the third option is achieved by the fact that in a piston machine containing cylinders located through a separating partition one above the other, in which the pistons of the cylinders of the first row are connected by rods to the pistons of the cylinders of the second row, and the working cylinder is doubled and has inlet and outlet windows and a common combustion chamber communicating its working cavities, which are located on both sides of the partition, according to the invention, the working cavities of the cylinders of the first row are flow-through and connected from the side gas inlet and outlet with working cavities of the second row cylinders, and the inlet and outlet windows of the first row cylinders are made in the upper part of the cylinder above the piston at its position at top dead center.

The piston machine in the embodiment of claim 1 and 2 is illustrated in FIG. 1-5 and has the following list of positions:
1 - dual slave cylinder;
2 - the piston of the left cylinder;
3 - the piston of the right cylinder;
4 - cavity of the left cylinder;
5 - cavity of the right cylinder;
6 - channel connecting the cavity 4 and 5;
7 - inlet window of cylinder 1;
8 - exhaust window of cylinder I;
9 - intake chamber;
10 - exhaust chamber;
11 - a partition separating the chambers;
12 - the seal of the septum;
13 - a camshaft;
14 - shaft bearings 12;
15 - a drive pulley of a shaft 12;
16 - spool valve of the intake chamber;
17 - spool valve of the exhaust chamber;
18 - the outlet window of the valve 16;
19 - inlet window of the spool 17;
20 - pressure seat of the spool 16;
21 - a window of a saddle 20;
22 - pressure seat of the valve 17;
23 - a saddle window 22;
24 - elastic cushion cushion saddles 20 and 22;
25 - bypass channel from the chamber 9 into the cavity 5;
26 - bypass channel from the cavity 4 to the chamber 10;
27 - spark plug or nozzle;
28 - supercharger;
29 - inlet window of the intake chamber;
30 - exhaust window of the exhaust chamber;
31 - engine crankshaft;
32 - crank;
33 - oil-filled crankcase of the movement mechanism.

 The engine has at least two adjacent interconnected working cylinders with a common combustion chamber, in which one cylinder has inlet windows and the other cylinder has outlet windows. Cylinder pistons move in one direction. The principle of operation of a multi-cylinder engine with an even number of cylinders will not differ from an engine having two adjacent interconnected cylinders, and therefore a two-cylinder engine is proposed for consideration.

 The engine shown in FIG. 1 has two adjacent interconnected cylinders 1, in which pistons 2 and 3 move. Cavities 4 and 5 of working cylinders are formed above the pistons 2 and 3, which are interconnected by a channel 6. Two adjacent interconnected cylinders can be considered as one twin cylinder, which has a common combustion chamber and one for two cylinders spark plug or nozzle for fuel injection 27. The engine has one inlet chamber 9 and one exhaust chamber 10. Through the chambers 9 and 10 there passes a wire shaft 13 installed in the bearings 14. The shaft 13 is rigidly securing enes pulley 15 cooperating with a toothed belt or chain, and the intake valve 16 and the spool chamber 17 release chamber. A window 18 is made on the cylindrical surface of the spool 16, and a window 19 is made on the surface of the spool 17. A saddle 20 having a window 21 is pressed against the cylindrical surface of the spool 16 and a saddle 22 having a window 23 is pressed against the cylindrical surface of the spool 17. Seats 20 and 22 are pressed to the spools 16 and 17 is carried out by elastic pillows or conventional spring-loaded pillows. The design of the hold-down seats can be different. In particular, the seats can be made of anti-friction materials that do not require lubrication, for example, based on graphitofluoroplast. The inlet chamber 9 has an inlet port 29, and the exhaust chamber 10 has an outlet port 30. A blower 28 can be connected to the inlet chamber. An ignition plug 27 or a fuel injector is connected to the cylinder 5 in the embodiment of using the piston machine as an internal combustion engine.

 If the cylinders were not dual, one would have to have one inlet chamber and one exhaust chamber for each cylinder. Accordingly, two inlet chambers and two exhaust chambers would be required for two cylinders. In addition, in addition to reducing the number of chambers, a twin cylinder improves the purge conditions of a two-stroke engine.

 The principle of operation of the engine shown in FIG. 1: as a result of the rotation of the slide valves, the windows 18 and 19 of the slide valves are periodically aligned with the windows 7 and 8 of cylinder 1. Depending on the length of the windows 18 and 19 along the arc of the circumference of the slide valves and their placement on the cylindrical surface of the slide valves, the angle of rotation of the shaft can be a predetermined diagram of the distribution of liquid or gas is implemented depending on the purpose of the piston machine.

 The phase diagrams of the distribution of a liquid or gaseous medium depending on the purpose of the piston machine are shown in FIG. 2, 3, 4 and 5.

 The four stroke engine variant has a timing diagram shown in FIG. 2.

A four-stroke engine is characterized by the fact that it has a full cycle of work in two revolutions of the engine shaft. Therefore, the gear ratio for rotation from the engine shaft to the camshaft is set to two to one. Accordingly, in two turns of the shaft, the spool valves make one revolution. The diagram of the valve timing shows that for one revolution of the spool the piston twice approaches the TDC and BDC, and a 180 ^o rotation of the engine shaft corresponds to a 90 ^o rotation of the spool valve. Shown in FIG. 2, the position of the slide valves in the angle of rotation of the shaft corresponds to the position of the piston in the BDC. Spool valves rotate clockwise.

When the piston moves from BDC to BDC in the exhaust chamber, the seat window 20 is aligned with the spool window 16, which has a circumference of 90 ^° . This means that when the piston passes from the BDC to the TDC, the gas throughout the entire stroke of the piston enters from the cylinder cavity into the exhaust chamber 8, and then through the window 27 goes to the exhaust, i.e., cylinder 1 is completely cleaned of burnt gases. At the same time, the spool 13 of the inlet chamber 8 is rotated 90 ^° . When the piston approaches TDC, the window 20 closes and the gas stops flowing out of the cylinder. At this point, in the inlet chamber 7, the window 13 of the spool 13 approaches the window 18 of the seat 17. There is a combination of windows and a suction cycle is carried out during the piston from TDC to BDC, and gas from the atmosphere or from the blower 25 through the window 29 enters the inlet chamber 7, and then through the windows 18 and 21, through the channel 25 and the window 7 enters the cylinder 1. The cycle of suction in the cylinder occurs throughout the entire piston stroke from TDC to BDC, because the window 18 has a circumferential arc length of 90 ^o . When the piston approaches the BDC, the windows 18 and 21 are closed. Further, during the piston stroke from BDC to BDC, gas compression occurs in the cylinder, since all windows in the cylinder at this stroke are closed. In the TDC of the piston, the fuel mixture is forced to ignite from the spark plug 27 or self-ignites when fuel is supplied through the nozzle 27. The gas expands during combustion and the piston travels from TDC to BDC. When the piston is in the BDC or somewhat earlier, the holes 19 and 23 in the exhaust chamber are combined, and the exhaust gas from the cylinder is exhausted and the cylinder begins to clean due to the movement of the piston from BDC to TDC. Further, all cycles of the four-stroke engine are repeated.

 In FIG. 3 shows a valve timing diagram when using a piston engine as a two-stroke internal combustion engine (ICE). At ДДВС the full cycle of work occurs for one revolution of a shaft of the engine. Therefore, the motor shaft and spool valves must rotate synchronously. The option is considered when the rotation of the motor shaft is clockwise. Shown in FIG. 3, the position of the slide valves in the angle of rotation of the shaft corresponds to the position of the piston in the HMT.

The diagram shows that in this position of the piston, the window 19 of the seat of the exhaust chamber is open and the release of burnt gases from the cylinder continues. At the same time, since the total length of the window 19 along the circular arc on the cylindrical surface of the spool 17 is α ₁ + α ₂ , it can be seen from the diagram that the exhaust gas release from the cylinder started earlier before the piston approached the BDC at the shaft rotation angle α ₂ . After turning the shaft of the spool valve 17 through an angle α _{1, the} window 21 of the seat 20 of the intake chamber is still closed. With further rotation of the spool valve 17 by an angle α ₂ , and the spool valve 16 by an angle α _{3, the} windows 23 and 21 will open, and the cylinder will be purged with fresh gas. After turning the spool valve 17 through the angle α ₂ and the spool valve 16 through the angle α _{3, the} window 23 closes, gas out of the cylinder stops and the cylinder begins to fill through the window 21 with excess gas pressure, which can create a supercharger 28. Duration of filling the cylinder with excess pressure will correspond to the rotation time of the spool valve 16 at an angle α ₄ . Such an alternation of opening and closing of the inlet 21 and outlet windows 23 allows for efficient direct-flow purge of the cylinder in the direction of the arrow in FIG. 3 and fill the cylinder after closing the window 23 with excess pressure.

 After filling the cylinder with a fresh portion of gas, the piston continues to move from BDC to TDC with windows 21 and 23 closed and a compression process occurs. At TDC, there is a forced ignition of the working mixture from a spark plug or self-ignition in the diesel version and gas expansion and piston stroke start before opening window 23. Then the burnt gases are released, the cylinder is purged and filled with excess pressure, and the engine operation is repeated.

 In FIG. 4 shows a gas distribution phase diagram in the case of using a piston machine as a reciprocating compressor (PC) to compress gas or to suck out gas and create a vacuum in the system (vacuum compressor).

The full cycle of the PC occurs in one revolution of its shaft. Therefore, the PC shaft and spool valves must rotate synchronously, for which the gear ratio for rotation from the PC shaft to the spool valve shaft is taken one to one. The option is considered when the rotation of the shaft is in the clockwise direction. Shown in figure 4, the position of the slide valves in the angle of rotation of the shaft corresponds to the position of the piston in the BDC. The diagram shows that in this position of the spool valves, the windows 21 and 18 are closed. When the piston moves from BDC to TDC and the spool valve 16 rotates 180 ^°, window 21 remains closed throughout the entire stroke of the piston. When turning the spool valve 17, the window 23 remains closed until the combination of windows 19 and 23 begins. During this time, the spool valve 17 rotates through an angle of 180-α ^° . At this time, the piston goes to TDC and compresses the gas in cylinder 1 by the calculated value. That is, there is a process of preliminary compression of gas according to the principle that is used, for example, in screw compressors. The value of the preliminary compression is calculated and is selected so that it corresponds to the specified pressure in the system on which the PC will work.

The amount of pre-compression is a function of the degree of compression of the gas that will be created in the cylinder before opening the outlet port 23. When the slide valve 17 is rotated by an angle greater than 180-α ^° , the windows 19 and 23 will begin to align, and the compressed gas will be pushed into the exhaust chamber and further into the system, where the same design pressure should be. The ejection time will correspond to the rotation time of the spool 17 by an angle α ^° , when the window 23 is closed by the cylindrical surface of the spool valve 17. The expulsion of the compressed gas from the cylinder will end when the piston approaches TDC. At this point, the window 18 of the spool valve 16 will fit to the window 21 and when the piston moves from the upper dead center to the upper borehole, the process of gas suction into the cylinder begins, which will continue throughout the entire stroke of the piston until it arrives at the lower borehole. During this time, the spool valve 16 will rotate 180 ^o . After the end of the suction cycle, the window 21 closes and the piston from the BDC goes to TDC, i.e. gas compression will begin, and the entire PC operation cycle will be repeated.

 In the case of connecting to the inlet chamber 9 of the compressor 28, the compressor capacity can be increased by a value proportional to the excess pressure that will be created in front of the inlet window 7 of the cylinder 1.

 Figure 5 shows a phase diagram of the distribution in the case of using a piston machine as a piston pump for pumping a liquid incompressible medium. The full cycle of operation of the monopole occurs in one revolution of its shaft. Therefore, the PN shaft and slide valves must rotate synchronously, for which the gear ratio for the rotation of the PN shaft to the shaft of the slide valves is taken one to one. The option is considered when the rotation of the shaft is in the clockwise direction. Shown in figure 5, the position of the slide valves in the angle of rotation of the shaft corresponds to the position of the piston in the BDC.

The diagram shows that in this position of the piston the opening of the window 21 ends, that is, the suction of the liquid medium into the cylinder 1 ends and the window 23 begins to open, which means that the cycle of pushing the medium from the cylinder 1 to the exhaust chamber 10 begins. the windows 18 of the spool valve 16 of the intake chamber 9 and the arc of a circle of the window 19 of the spool valve 17 of the exhaust chamber 10 are 180 ⁰ . Therefore, the inlet of the liquid medium into the cylinder 1 is on the entire pumping stroke of the piston during its movement from the top dead center to the bottom dead center.

 Also, the release of liquid medium from cylinder 1 occurs throughout the ejection stroke of the piston as it moves from BDC to TDC.

 The proposed piston engine, which can operate as a four-stroke or two-stroke internal combustion engine, as well as a compressor for compressing gas or a pump for pumping a liquid medium, have a new design of the distribution mechanism.

If we compare the proposed piston engine in the variant of a four-stroke engine with the already known four-stroke engines, in which the distribution mechanism includes cam camshaft, rocker arms, lifting valves, oil seals and springs, then the following advantages of the proposed design can be noted:
- increased reliability and durability, because there is no camshaft of complex shape, which experiences dynamic pulsating loads, is subject to wear and requires heavy lubrication;
- inertial valves of the lifting type are replaced by inertialess spool valves of rotational action. As a result, the engine speed can be increased and its mass reduced at a given power;
- reduced noise level of the gas distribution mechanism, as it does not experience dynamic loads due to the lack of cams and does not require adjustment of the gaps between the valves and pushers to compensate for the wear of rubbing surfaces during operation;
- the spool valve is in lighter operating conditions and does not require lapping during operation, as the saddle is self-gripping;
- lower energy costs are required to drive spool valves than to drive lift valves using a cam shaft;
- the spool valve is full bore and has less gas-dynamic resistance. To fully open the inlet and outlet windows, a smaller angle of rotation of the shaft is required, i.e. on the whole cycle of operation they are completely open, and therefore the cylinder filling factor and engine power increase;
- less auxiliary parts such as seals, springs.

If we compare the proposed piston engine in the variant of a two-stroke engine with the known two-stroke engines, then the following advantages can be canceled:
- after purging the cylinder, it is filled with the exhaust windows closed, which allows using the charge to obtain a cylinder fill factor of more than one. As a result, the efficiency and engine power increase;
- on the cylinder wall in its lower part there are no inlet and outlet windows. As a result, the removal of crankcase oil through the windows is eliminated, there is no need to increase the length of the pistons and cylinders. Typical cylinder blocks and pistons from any four-stroke engine can be used;
- improves the scheme of purging the cylinder from residual gases, which increases the frequency of exhaust gases and engine efficiency;
- reduced wear of the piston rings, because they do not run across the inlet and outlet windows; special fixing of the piston rings on the piston from turning is not required;
- four-stroke engines can be transferred to a two-stroke cycle with minimal cost, because the design of the cylinder block and pistons remains unchanged. Only the cylinder cover changes. In this case, engine power is increased by two or more times.

If we compare the proposed reciprocating machine in the compressor variant with the known reciprocating compressors, then the following advantages can be noted:
- there are no self-acting lifting valves with inertial working plates, which under the conditions of reliability limit the speed of rotation of the compressor. The proposed compressor version has inertia-free spool valves and makes it possible to increase the compressor rotation speed by an order of magnitude and, therefore, reduce its cost and weight several times at a given capacity;
- the absence of self-acting valves having shock working plates, can significantly reduce the noise level of the compressor;
- reduced resistance of the gas path, because inlet and outlet windows are full bore throughout the entire opening cycle, which improves the economic performance of the compressor;
- the lack of self-acting valves with lifting plates allows the use of a compressor to compress contaminated gases, since the spool valves are full bore and self-cleaning;
- increases the reliability of the compressor and facilitates its maintenance during operation, because there are no self-acting valves requiring frequent repairs and replacement of shock plates;
- the absence of self-acting valves and the effect of scraping their working plates on the saddle allows the compressor to be used for operation without lubricating the cylinders, which allows it to be used in explosive production, which does not allow the presence of oil.

Advantages of a piston machine in the variant of a piston pump in comparison with the known piston pumps for pumping a liquid medium:
- the absence of self-acting valves or forced-action valves allows pumping a liquid medium with large fractions of solid parts, since the possibility of these particles getting between the valve and the seat is excluded. Spool valves are self-cleaning;
- the absence of shock valves increases the reliability of the piston pump and allows you to increase its speed of rotation. As a result, at a given performance, the dimensions and weight of the pump are reduced, as well as its cost in the manufacture.

 If in a piston machine with one cylinder one inlet chamber and one outlet chamber are required, then if there are two adjacent cylinders, the number of chambers can be reduced, i.e. instead of two inlet chambers and two exhaust chambers, one inlet and outlet chamber, each of which will work on two cylinders.

An embodiment of the piston machine according to paragraphs 1 and 3 of the claims is illustrated in Fig.6 and 7, which have the following list of positions:
1 - left working cylinder;
2 - the working cylinder is right;
3 - the piston of cylinder 1;
4 - the piston of the cylinder 2;
5 - cylinder cavity 1;
6 - the cavity of the cylinder 2;
7 - inlet window of cylinder 1;
8 - exhaust window of cylinder 1;
9 - inlet window of cylinder 2;
10 - exhaust window of the cylinder 2;
11 - inlet chamber;
12 - exhaust chamber;
13 - a partition separating the chambers;
14 - a seal of a partition;
15 - drive shaft spools;
16 - shaft bearings 15;
17 - a pulley of a shaft 15;
18 - spool valve of the intake chamber, right;
19 - spool valve of the intake chamber left;
20 - spool valve of the exhaust chamber, right;
21 - spool valve of the exhaust chamber left;
22 - the outlet window of the valve 18;
23 - the outlet window of the spool 19;
24 - inlet window of the spool 20;
25 - inlet window of the spool 21;
26 - pressure seat of the valve 18;
27 - a window of a saddle 26;
28 - pressure seat of the spool 19;
29 - a window of a saddle 28;
30 - pressure seat of the spool 20;
31 - window saddle 30;
32 - pressure seat of the spool 21;
33 - a window of a saddle 32;
34 - elastic seat cushion;
35 - bypass channel from the chamber 11 into the cavity 6;
36 - bypass channel from the cavity 6 to the chamber 12;
37 - bypass channel from the chamber 11 into the cavity 5;
38 - bypass channel from the cavity 5 to the chamber 12;
39 - spark plug or nozzle;
40 - supercharger;
41 - inlet window of the chamber 11;
42 - exhaust window of the camera 12;
43 - engine crankshaft;
44 - crank;
46 - oil-filled crankcase movement mechanism.

 The two-stroke engine according to the described embodiment contains two adjacent working cylinders independent from each other, each of which has its own inlet and outlet windows, and their pistons counter-move and work in antiphase with respect to each other. With this operation of the cylinders, it becomes possible to have one inlet chamber and one exhaust chamber for two cylinders. The engine can be multi-cylinder with an even number of cylinders, of which every two adjacent cylinders have pistons that counter-move. The principle of operation of such a multi-cylinder engine will not differ from an engine that has two adjacent cylinders with pistons that counter-move, and therefore it is sufficient to consider the principle of operation using an example of a two-cylinder engine.

The engine contains a left working cylinder 1 and a right working cylinder 2, in which the pistons 3 and 4 are moved. Each piston is connected to its crank 44. Due to the displacement of the cranks of the pistons 3 and 4 relative to each other by 180 ^o along the angle of rotation of the shaft of the pistons 3 and 4 make oncoming motion and work in antiphase to each other. A cylinder cavity 5 is formed above the piston 3, and a cylinder cavity 6 is formed above the piston 4. The cylinder 2 has an inlet 9 and an exhaust window 10. The cylinder 1 has an inlet 7 and an exhaust window 8. The cylinders operate independently of each other and each of them has your spark plug or injector for fuel injection 39 (in the context of the left cylinder, the candle is not shown).

 An intake chamber 11 is installed above the cylinder 2, and an exhaust chamber 12 is installed above the cylinder 1. The chambers 11 and 12 are isolated from each other and separated by a partition 13. Two spools 18 and 19 are placed in the inlet chamber 11, and two spools are placed in the exhaust chamber 20 and 21. The spools have a rotation drive from the shaft 15, which is connected by rotation with the pulley 17 to the motor shaft 43. The gear ratio for rotation from the motor shaft to the spool drive shaft for the two-stroke engine, compressor and pump is set to one to one, and for even rehtaktnogo engine two to one. The engine embodiment of FIG. 6 and 7 differs from the engine variant in FIG. 1 in that two spools are placed in the inlet chamber and the exhaust chamber. In this case, in the intake chamber and exhaust chamber, each spool works on its own cylinder.

For convenience of consideration, in Fig. 6, the moment is recorded when the piston of the left cylinder is in the upper dead center, and in Fig. 7, after the engine shaft is rotated 180 ^{°, the} piston of the left cylinder goes into the BDC. These two positions of the pistons allow us to consider the main phases of the operation of a two-stroke engine.

 The principle of operation of the engine in the described embodiment is as follows.

When the position of the piston 4 in the BDC (Fig.6) shows that the working stroke of the piston 4 and the burnt gas from the cavity 6 through the exhaust window 10, the bypass channel 36, the window 31 and the window 24 enters the exhaust chamber, and then through the window 42 into the atmosphere. At the same time or with delay, depending on the location of the windows 22 on the cylindrical surface of the spool 18 and the windows 24 on the cylindrical surface of the spool 20 (see Fig. 3 diagram of the valve timing) gas from the blower 40 through the window 41, window 22, window 27 and window 9 enters into cavity 6 and pushes out the remains of burnt gases, i.e. The cylinder 2 is purging and filling with fresh gas. Then, when the piston 4 went to the TDC, when turning the spools 18 and 20, the windows 31 and 27 are closed. In the cylinder 2, gas compression begins, and in the cylinder 1, after the mixture ignites, the gas expands, and the piston 3 begins its stroke. After the piston 3 approaches the BDC (Fig. 7), the purging and filling of cylinder 1 begins in the same way as it did in cylinder 2. That is, the cycle of operation of the cylinder 1 and 2 alternates through 180 ^{o the} angle of rotation of the shaft.

 In all embodiments, to ensure the tightness of the closing of the inlet and outlet windows 9, 10, 7 and 8 of the cylinders 1 and 2, the gas path from the windows to the spools has a heat-resistant elastic clamping gasket 34, which is installed under the seats 32, 30, 28 and 26. As a result, these saddles are constantly pressed against the spools 20, 21, 19 and 18 and compensate for possible wear of the saddles.

 It is assumed that the annular saddles in contact with the cylindrical surface of the spools are made of heat-resistant antifriction material type f4k20, which does not require additional lubrication for its work in the friction units. To reduce the wear of saddles and facilitate their work, the spool windows can be made not continuous, but in the form of a grid or with partitions, which is easy to accomplish using modern manufacturing technologies, for example, using laser metal flashing. In the variants shown in figures 1, 6 and 7, the principle of the operation of a two-stroke engine is considered, but structurally with the appropriate arrangement of windows 24, 25, 23 and 22 on the cylindrical surface of the spools according to the angle of rotation of the shaft, the proposed piston machine can operate as a four-stroke engine a compressor for compressing and suctioning gas or a pump for pumping liquid.

 The advantage of using spools is that they have a cylindrical shape and do not experience inertial loads when the shaft rotates, the spool windows contact the seat windows without dynamic loads, the possible wear of the seats is compensated by constantly pressing the seats to the spools with elastic linings that are under the saddles . The operation of the switchgear is completely silent and does not require any adjustment of the gaps during operation. In this design, the piston machine can operate at an increased rotational speed, which can significantly reduce the mass of the piston machine at specified power or performance parameters. The economic parameters of the reciprocating machine may be increased since it is possible to increase the bore sections of the inlet and outlet windows, which does not cause any dynamic and inertial loads on the gas distribution mechanism. In contrast to the cam principle of opening valves for lifting action, the windows open immediately to the entire passage area.

 If we compare a reciprocating piston machine with a compressor compared to compressors with self-acting valves experiencing high dynamic loads, a piston machine without self-acting valves can have an order of magnitude higher rotation speed than existing compressors and can compete with the specific gravity per unit of output screw and centrifugal valves, as much more economical due to the lack of design gas gaps and the reduction of gas leaks in the opposite direction, and also has a lower manufacturing cost. As a result, screw and centrifugal compressors lose their main advantage over the proposed design of a reciprocating compressor - this is the lack of self-acting valves.

 As the closest analogue according to the option described in paragraphs 4–7 for a piston machine used as a two-stroke internal combustion engine (ДДВС), the ДДВС according to the patent of the Russian Federation [1] can be considered.

The disadvantages of the prototype are as follows:
- inlet and outlet windows are located on the cylinder wall in its lower part and are periodically blocked by the piston during its movement. As a result, the crankcase oil may be carried through windows. To reduce the entrainment of crankcase oil, the length of the pistons and cylinders is increased, and additional piston rings are installed on the piston in its lower part;
- when the piston moves, its piston rings run across the windows. As a result, the wear of the piston rings increases and their special fixing on the piston from turning is required so that the locks of the piston rings do not coincide with the windows. Passing locks of piston rings through windows can cause damage to the piston rings.

 Such an engine is a prototype, as well as the inventive design of a piston machine for use as a two-stroke internal combustion engine, contains a working cylinder with inlet and outlet windows.

 The objective of the invention in part of the second option is also the refusal to place the inlet and outlet windows in the lower part of the cylinder wall. As a result, engine reliability is improved and its economic parameters are improved.

The essence of the piston machine according to claims 4-7 is illustrated in FIG. 8, 9, 10, which have the following list of positions:
Option items 4, 5 and 7
1 - left working cylinder;
2 - the working cylinder is right;
3 - the piston of cylinder 1;
4 - the piston of the cylinder 2;
5 - cylinder cavity 1;
6 - the cavity of the cylinder 2;
7 - inlet window of cylinder 2;
8 - exhaust window of cylinder 1;
9 - channel communicating cavities 5 and 6;
10 - a spark plug or nozzle;
11 - dividing wall;
12 - intake chamber;
13 - exhaust chamber;
14 - guide cylinder (spool) of the chamber 12;
15 - guide cylinder of the chamber 13;
16 - a glass (spool) of the cylinder 14;
17 - a glass cylinder 15;
18 - supercharger;
19 - inlet window of the chamber 12;
20 - the outlet window of the camera 13;
21 - inlet window of the guide cylinder 15 of the exhaust chamber;
22 - exhaust window of the guide cylinder 14 of the intake chamber;
23 - the inlet window of the glass 17;
24 - exhaust window of the glass 16;
25 - bypass channel from the chamber 12 into the cavity 6;
26 - bypass channel from the cavity 5 to the chamber 13;
27 - a rod connecting the piston and the glass;
28 - engine crankshaft;
29 - crank;
30 - oil-filled crankcase movement mechanism.

 In FIG. 8 shows an engine according to claims 4, 5 and 7, having at least two adjacent interconnected working cylinders with a common combustion chamber, in which one cylinder has inlet windows and the other cylinder has outlet windows. The pistons of the cylinders move in one direction, and each of them is connected with its own crank. When the cranks deviate from each other by an angle α in the direction of rotation of the shaft, the opening and closing of the outlet windows with respect to the inlet windows can be achieved ahead of the movement in the direction of rotation of the cylinder piston with the outlet windows. An external boost source, such as a turbocharger, was used to purge and fill the cylinders. The principle of operation of a multi-cylinder engine with an even number of cylinders will not differ from an engine having two adjacent interconnected cylinders, and therefore a two-cylinder engine is proposed for consideration.

 The engine shown in FIG. 8 has two adjacent interconnected cylinders 1 and 2, in which the pistons 3 and 4 are connected, connected with the cranks 29. Cavities 5 and 6 of the working cylinders are formed above the pistons 3 and 4, which are interconnected by a channel 9. Cylinder 2 has inlet windows 7 and cylinder 1 has exhaust ports 8. Cylinders 1 and 2 can be considered as one twin cylinder, which has a common combustion chamber and one spark plug or two nozzle for injecting fuel 10. Two cylinders are mounted above cylinders 1 and 2 through a partition 11 intake that has an intake a vent window 19, and an exhaust chamber 13, which is isolated from the intake chamber 12, and which has an exhaust port 20. A blower 19 is connected to the intake window 19 of the intake chamber 12. The intake chamber has an exhaust port 22, which is connected to the cavity 6 of the cylinder 2 by the bypass channel 25 and the exhaust chamber has an inlet 21, which is connected to the cavity 5 of cylinder 1 by the bypass channel 26. Inside the intake and exhaust chambers, the shutters 16 and 17 are moved, which are connected via piston rods 27 to the pistons of the cylinders. The flaps 16 and 17 serve to block the windows 21 and 22 and are made, for example, in the form of hollow spools of round or rectangular cross section, which are in contact with the guide walls 14 and 15 of the inlet and outlet chambers. In the upper part of the shutters in the axial direction, windows 23 and 24 are made, which, when the pistons are in the BDC, coincide with the windows 21 and 22. When the pistons move to the TDC, the windows 21 and 22 are overlapped by the shutters. The seal between the windows 21 and 22 and the surface of the shutters 16 and 17 at the moment of closing the windows 21 and 22 is achieved, for example, due to a special elastic seal, which is made on the guide walls 14 and 15.

 The stages of the working cycle of a two-stroke engine depend on the position of the pistons with respect to TDC and BDC. In FIG. 8 shows the stage of the duty cycle when the pistons 3 and 4 are in the BDC.

 The principle of operation of the engine is as follows.

 When the piston is in the BDC, the windows 21 and 23, as well as the windows 22 and 24 are combined. This means that the release of burnt gases from cavities 5 and 6 has ended. The release of gas occurs in the following sequence. First, from the cavity 6 through the channel 9. Then from the cavity 5 through the window 8, the bypass channel 26, windows 21 and 23, the exhaust chamber and then through the window 20 into the atmosphere.

 At the same time, sequential purging of the working cavities of the cylinder in the direction takes place - gas flows from the supercharger 18, through window 19, windows 24 and 23, the bypass channel 25, window 7, cavity 6 channel 9, cavity 5, window 8, bypass channel 26, window 21 and 23, the exhaust chamber and further through the window 20 into the atmosphere.

 The purging and filling of cavities 5 and 6 continues even when the pistons begin to move to TDC, until windows 21 and 22 overlap. By shifting the cranks in the angle of rotation of the shaft, it is possible to ensure that the opening and closing of the outlet window 21 is ahead of the inlet window 22.

Then, after closing the window 21, the filling of the cavities will continue through the still open window 22, which will create conditions for filling the working cavities with excess pressure, which can be provided by the supercharger 18. After closing the windows 21 and 22 as a result of the movement of the pistons 3 and 4 to the TDC in the cavities 5 and 6, compression begins. When pistons approach TDC,
ignition of the mixture from the candle 10 or self-ignition of the mixture after fuel injection through the nozzle (diesel version). The gas expands, the stroke of the pistons begins, and the latter move toward the BDC. When you open the window 21 is the release of burnt gases, purging and filling cavities 5 and 6 through the window 22, and the process is repeated every gas when the engine shaft is rotated 360 ^o .

The essence of the embodiment of the piston machine in paragraphs 4, 6 and 7 is illustrated in FIG. 9 and 10, which have the following list of positions:
1 - left working cylinder;
2 - working cylinder right;
3 - the piston of cylinder 1;
4 - the piston of the cylinder 2;
5 - cylinder cavity 1;
6 - the cavity of the cylinder 2;
7 - inlet window of cylinder 2;
8 - exhaust window of the cylinder 2;
9 - inlet window of cylinder 1;
10 - exhaust window of cylinder 1;
11 - a spark plug or nozzle;
12 - dividing wall;
13 - intake chamber;
14 - exhaust chamber;
15 - guide cylinder of the intake chamber;
16 - guide cylinder of the exhaust chamber;
17 - a glass (inlet chamber spool);
18 - a glass of the exhaust chamber;
19 - inlet window of the intake chamber;
20 - exhaust window of the exhaust chamber;
21 - left inlet window of the exhaust chamber;
22 - inlet window of the exhaust chamber, right;
23 - left inlet exhaust chamber window;
24 - outlet window of the intake chamber, right;
25 - the upper window of the glass 17;
26 - window lower glass 17;
27 - the upper window of the glass 18;
28 - window lower glass 18;
29 - bypass channel from the inlet chamber to the cavity 6;
Z0 - bypass channel from the cavity 6 to the exhaust chamber;
31 - bypass channel from the inlet chamber to the cavity 5;
32 - bypass channel from the cavity 5 to the exhaust chamber;
33 - a rod connecting the piston and the glass;
34 - engine crankshaft;
35 - crank left;
36 - crank right;
37 - oil-filled crankcase of the movement mechanism;
38 - supercharger.

 In FIG. 9 and 10 depict a two-stroke engine according to paragraphs 4, 6 and 7, containing two adjacent independent working cylinders, each of which has its inlet and outlet windows, and their pistons counter-move and work in antiphase with respect to each other. Pistons are connected by means of rods to dampers that move in the inlet and outlet chamber and overlap the channel windows that are connected to the inlet and outlet windows of the cylinders, the engine can be multi-cylinder with an even number of cylinders, of which every two adjacent cylinders have reciprocating pistons .

 The principle of operation of such a multi-cylinder engine will not be different from an engine having two adjacent cylinders with pistons that counter-move, and therefore it is sufficient to consider the principle of engine operation using an example of a two-cylinder engine.

The engine of FIG. 9 and 10 contains a left working cylinder 1 and a right working cylinder 2, in which the pistons 3 and 4 move. Each piston is connected to its crank 35 and 36. Due to the displacement of the cranks of the pistons 3 and 4 relative to each other by 180 ^o the rotation of the shaft, the pistons 3 and 4 performs oncoming motion and work in antiphase to each other. A cylinder cavity 5 is formed above the piston 3, and a cylinder cavity 6 is formed above the piston 4. The cylinder 2 has an inlet window 7 and an outlet window 8. The cylinder 1 has an inlet window 9 and an outlet window 10. The cylinders 1 and 2 operate independently of each other, and each of them has its own spark plug or nozzle for injecting fuel 11. Above the cylinders 1 and 2, an inlet chamber 13, which has an inlet window 19, and an outlet chamber 14, which has an outlet window 20, is isolated from the inlet chamber 13. To the inlet window 19 of the inlet chamber 13 a supercharger 38 is connected. The inlet chamber has an outlet port 24, which is connected to the cavity 6 of the cylinder 2 using the bypass channel 29, and the exhaust chamber has an inlet port 21, which is connected to the cavity 5 of the cylinder 1 using the bypass channel 32. Inside the intake and exhaust chambers the shutters 17 and 18 are moved, which are connected by means of rods 33 for movement with the pistons of the cylinders. The dampers 17 and 18 serve to block the windows 21 and 24 and are made, for example, in the form of spools of round or rectangular cross section, which are in contact with the guide walls 15 and 16 of the intake and exhaust chambers. The axes 25 and 27 are made in the upper part of the shutters in the axial direction, which, when the pistons are in the BDC, coincide with the windows 21 and 24. When the pistons move to the TDC, the windows 21 and 24 are overlapped by the shutters. The seal between the windows 21 and 24 and the surface of the shutters 17 and 18 at the moment of closing the windows 21 and 24 is achieved, for example, due to a special elastic compression seal, which is made on the guide walls 15 and 16.

 The stages of the working cycle of a two-stroke engine depend on the position of the pistons with respect to TDC and BDC. In FIG. 9 shows the stage of the duty cycle when the piston 3 is located at TDC and the piston 4 at BDC.

 The principle of operation of the engine is as follows.

 When the position of the piston 4 in the BDC, the windows 21 and 27, as well as the windows 25 and 24 are combined. This means that the release of burnt gases from the cavity 6 has ended. The release of gas occurs in the following sequence. Through the window 8, the bypass channel 30, the window 22 and the window 28 into the exhaust chamber 14 and then through the window 20 to the atmosphere. At the same time, the cavity 6 is purged in the direction — gas flows from the supercharger 38 through window 19, windows 25 and 24, bypass channel 29, window 7, cavity 6, window 8, bypass channel 30, windows 22 and 28, exhaust chamber, and then into the atmosphere . The purging and filling of the cavity 6 continues even at the beginning of the movement of the piston 4 to the TDC until the windows 22 and 24 overlap. By shifting the cranks of the pistons in the angle of rotation of the shaft, it is possible to ensure that the opening and closing of window 22 is ahead of window 24. Then, after closing the window 21, the filling of the cavity 6 will continue through the still open window 24, which will create conditions for filling the cavity 6 with excess pressure, which can be provided by the supercharger 38. After the windows 22 and 24 are closed as a result of the movement of the piston 4 towards the upper center, compression begins.

 While the piston 4 goes up to compression, the piston 3 makes a working stroke as a result of the expansion of the gas after its ignition in the cavity 5.

When the piston 4 approaches the TDC, the mixture is ignited in the cavity 6, the gas expands and the piston 4 starts working. At this moment, the piston 3 is in the BDC and the cavity 5 is purged and filled with fresh gas. Thus, the cycles in the cylinders 1 and 2 are repeated, and the working stroke of each piston occurs through 360 ^{o of the} angle of rotation of the shaft, and the working strokes of the pistons in a two-cylinder two-stroke engine, shown in FIG. 9 and 10, are repeated through 180 ^{o the} angle of rotation of the shaft.

 The engine in this design will have high reliability, because It has an oil-filled crankcase of the movement mechanism and high efficiency, because when using fuel injection directly into the cylinder after the closed intake and exhaust windows, fuel losses through the windows are eliminated. In addition, the loss and removal of crankcase oil through the cylinder windows are eliminated, as the windows are in the upper part of the cylinder and do not overlap with the piston, i.e. lubrication conditions are the same as in a four-stroke engine.

 As the closest prototype for a piston machine used as a two-stroke internal combustion engine and described in paragraph 8 of the claims, the design of a two-row engine according to the patent of the Russian Federation can be considered [1].

 The disadvantage of the closest prototype is that in variants 1, 3, 4 and 5 of the prototype, the inlet and outlet windows of the engine cylinders are located in the lower parts of the cylinders above the piston at its position at bottom dead center (see Fig. 1, 3, 5, 11 , 13, 14, 15, 16, 17, 18, 19, 20, 21, 22 and 23 of the prototype). This arrangement of the windows entails the need to increase the length of the cylinders and the piston to close the windows when the pistons are in top dead center. Otherwise, there is a likelihood of oil being removed from the engine crankcase to the exhaust windows and fuel entering the engine crankcase through the intake ports, in addition, for the same reason, additional piston rings must be placed on the bottom of the piston skirt.

 Like the prototype, the proposed variant of the internal combustion engine contains working cylinders located one above the other through the separating partition, in which the pistons of the cylinders of the first row are connected by rods to the pistons of the cylinders of the second row, and the working cylinder is doubled and has inlet and outlet windows and a common combustion chamber that communicates its working cavity, which are located on both sides of the septum.

 The objective of the invention in part of the third option is additionally to simplify the design of the engine and reduce its specific gravity per unit of power, as well as increase efficiency and reduce consumption of crankcase oil.

 When performing the third embodiment, a two-row engine has at least two adjacent pairs of pistons, each of which has two pistons connected by a rod.

 In this case, the cylinders of the first row are separated from the cylinders of the second row by a partition. In the second row, the working cylinder of one pair of pistons has inlet windows, and the working cylinder of the second row of the other pair of pistons has outlet windows. The engine may be multi-cylinder, but then it must have an even number of piston pairs.

 To better fill the working cylinders, the crank of the piston of the cylinder with the outlet window may have a deviation in the angle of rotation of the shaft in the direction of rotation from the crank of the piston of the cylinder with the inlet window.

 As a result, the opening and closing of the outlet windows is prevented in relation to the inlet windows. Each pair of pistons is connected with its own crank and, depending on the location of the cranks relative to each other in terms of the angle of rotation of the shaft, can move in one or the opposite direction.

The stated essence of the piston machine according to paragraph 8 of the claims in embodiments 1, 2, 3 and 4 is illustrated in Figs. 11-15, which have the following list of positions:
Execution 1, 11 and 12
1 - working cylinder left of the first row;
2 - working cylinder, right, first row;
3 - the piston of cylinder 1;
4 - the piston of the cylinder 2;
5 - the cavity of the working cylinder 1;
6 - the cavity of the working cylinder 2;
7 - the inlet window of the cavity 5;
8 - the outlet window of the cavity 5;
9 - the inlet window of the cavity 6;
10 - the outlet window of the cavity 6;
11 - dividing wall;
12 - left-hand side working cylinder of the second row of the second row;
13 - the working cylinder of the bilateral action of the second row, right;
14 - the piston of the cylinder 12;
15 - the piston of the cylinder 13;
16 - the cavity of the working cylinder 12 above the piston;
17 - the cavity of the working cylinder 12 under the piston;
18 - the cavity of the working cylinder 13 above the piston;
19 - the cavity of the working cylinder 13 under the piston;
20 - the inlet window of the cavity 16;
21 - the outlet window of the cavity 16;
22 - the inlet window of the cavity 17;
23 - the outlet window of the cavity 17;
24 - bypass channel connecting the cavity 6 and 17;
25 - bypass channel connecting the cavity 5 and 16;
26 - the inlet window of the cavity 18;
27 - the outlet window of the cavity 18;
28 - the inlet window of the cavity 19;
29 - the outlet window of the cavity 19;
30 - bypass channel connecting the cavity 19 and 5;
31 - bypass channel connecting the cavity 18 and 6;
32 - engine crankshaft (piston movement mechanism);
33 - crank left;
34 - crank right;
35 - rods connecting the pairs of pistons;
36 - spark plug or nozzle;
37 - supercharger;
38 - oil-filled crankcase movement mechanism.

 In FIG. 11 and 12 depict a two-row engine in version 1, having at least two pairs of pistons, each of which has pistons connected by rods and connected to its crank.

The cranks of each two pairs of pistons have deviations between themselves in the angle of rotation of the shaft by 180 ^o or 180 + α ^° and provide oncoming movement of the pairs of pistons and the operation of their cylinders in antiphase with respect to each other. When the cranks deviate from each other by an angle of 180 + α ^° , the opening and closing of the outlet windows of the cylinder 12 is anticipated in relation to the inlet windows of the cylinder 13.

 The principle of operation of a two-row multi-cylinder engine with an even number of piston pairs (more than two) will not differ from a two-row engine having two interconnected pairs of pistons, and therefore, an engine with two pairs of pistons is proposed for consideration.

The principle of operation of such an engine can be considered according to the stages of the working cycle depending on the position of the pistons with respect to the bottom dead center (BDC) and top dead center (TDC) in the range from 0 ^o to 360 ^{o the} angle of rotation of the shaft, because in this interval, a complete six-hour cycle of the two-stroke engine in two cycles is performed, alternating through 180 ^o .

 11 and 12 show an embodiment 1 when all the cylinders are working, and all the cylinder cavities are purged from an external source, for example, from a supercharger.

In FIG. 11 shows the stage of the working cycle, when the pistons 3 and 14 of the left pair of pistons are suitable for BMT, and the pistons 15 and 4 of the right pair of pistons are suitable for BDC. Ha 12 shows the stage of the duty cycle when the pistons of the left and right pairs of pistons change places after the rotation of the engine shaft by 180 ^o .

 The engine in FIGS. 11 and 12 in the first row has single-acting cylinders 1 and 2, and in the second row are double-acting cylinders 12 and 13. Above the pistons 3 and 4 of the first row of cylinders, as well as above and below the pistons 14 and 15 of the second row of cylinders, cavities of the working cylinders are formed which have inlet and outlet windows.

 A blower 37 is used to purge and pressurize all the cavities of the working cylinders. The working cylinder of the cavity 18 (Fig. 11) has inlet windows 26 and exhaust windows 27. The working cylinder 2 of the cavity 6 has inlet windows 9 and exhaust windows 10. The working cylinder of the cavity 17 has inlets windows 22 and exhaust windows 23. Cavities 18 and 6 of the working cylinders are connected to each other bypass channel 31, and the cavities 6 and 17 are connected bypass channel 24. As a result, 3 cavities 18, 6 and 17 communicate with each other and have a common combustion chamber, and the working the cylinders of these cavities are enamel. In this case, the cavity 6 of the working cylinder 2 of the first row is flowing and is located between the cavities 18 and 17, which are from the cavity 6 in the second row on the other side of the partition 11.

 The working cylinder 13 of the cavity 19 (Fig. 12) has inlet windows 28 and exhaust windows 29. The working cylinder 1 of the cavity 5 has inlet windows 7 and exhaust windows 8. The working cylinder 12 of the cavity 16 has inlet windows 20 and exhaust windows 21. Cavities 19 and 5 are interconnected by the bypass channel 30, and the cavities 5 and 16 are interconnected by the bypass channel 25. As a result, the three cavities 19, 5 and 16 communicate with each other and have a common combustion chamber, and the working cylinders of these cavities are built. In this case, the cavity 5 of the working cylinder 1 of the first row, as well as the cavity 6, is flowing, because located between the cavities 19 and 16, which from the cavity 5 is located on the other side of the partition. Constructed working cylinders are equipped with spark plugs or nozzles for fuel injection 36.

 A distinctive feature of the engine according to claim 8 of the claims in execution 1 in comparison with the closest prototype (1) is that the working cylinders involved in the work are not double, but built. In this case, the cavities of the working cylinders of the first row are flowing, and their inlet and outlet windows are located in the upper part of the cylinders and do not overlap with the piston. This arrangement of the windows of the cylinders of the first row allows you to refuse to increase the length of the pistons and cylinders, and also eliminates the removal of oil from the crankcase, which occurs when the windows are located above the piston when it is in the BDC, as in the prototype. As a result, the design of the internal combustion engine is simplified, its reliability is increased and the specific gravity per unit of power is reduced, and the environmental frequency of the exhaust gases is increased and the crankcase oil consumption is reduced.

 The principle of operation of the engine in this design is as follows.

 In FIG. 11, the moment is recorded when the working stroke of the pistons 15, 4, and 14 ends in the constructed working cylinder containing interconnected cavities 18, 6, and 17 and the latter approach the BDC. Accordingly, the release of flue gases through windows 23 ends.

 At the same time, sequential purging of the cavities 18, 6 and 17 with fresh gas from the supercharger 37 takes place. At the beginning, gas flows from the supercharger 37 to the inlet ports 26, fills the cavity 18 and enters the cavity 6 through the bypass channel 31 and then enters the cavity 17 through the bypass channel 24 By the time the purges of the cavities 18, 6 and 17 are completed, the outlet windows 23 are closed and the inlet windows 26 are still open.

 As a result, an excess pressure is created in the cavities 18, 6 and 17, which can be created by the supercharger 37. At the same time, the fuel mixture ignites above the pistons 3 and 14 and under the piston 15. The gas expands and the pistons travel in a cylinder built with between each other, the cavities 5, 16 and 19. As a result, the pistons 3 and 14 of the left pair make a stroke and move down to the BDC, and the piston 15 of the right pair makes a stroke and moves up to the top dead center.

 First, windows 21 open (see FIG. 12) and the release of burnt gases occurs. Then, the inlet windows 28 begin to open and the cavities 19, 5 and 16 are purged. After the windows 21 are closed, the windows 28 are still open in the cavities 19, 5 and 16 and the pressure rises above atmospheric to the excess pressure created by the supercharger 37.

 Then again, the fuel mixture ignites already under the piston 14 and above the pistons 15 and 4. The left pair of pistons goes up to the TDC, and the right pair of pistons goes down to the BDC, and the process repeats. Such a two-row engine will have a specific gravity per unit of power, four or more times less than a single-row four-stroke engine of the same power.

Execution 2, Fig.13
1 - a double working cylinder of unilateral action of the first row;
2 - pistons of cylinder 1;
3 - cylinder cavity 1 left;
4 - the cavity of the cylinder 1 is right;
5 - inlet window of cylinder 1;
6 - exhaust window of cylinder 1;
7 - left-sided cylinder of the second row;
8 - double-acting cylinder of the second row, right;
9 - the piston of the cylinder 7;
10 - the piston of the cylinder 8;
11 - the cavity of the working cylinder 7 above the piston 9;
12 - the cavity of the working cylinder 7 under the piston 9;
13 - the cavity of the working cylinder 8 above the piston 10;
14 - the cavity of the working cylinder 8 under the piston 10;
15 - the inlet window of the cavity 11;
16 - the outlet window of the cavity 11;
17 - the inlet window of the cavity 13;
18 - the outlet window of the cavity 13;
19 - the inlet window of the cavity 14;
20 - the outlet window of the cavity 12;
21 - a bypass channel connecting the cavity 13 with the cavity 4;
22 - channel connecting the cavity 4 cavity 3;
23 - bypass channel connecting the cavity 3 with the cavity 11;
24 - channel connecting the cavity 14 and 12;
25 - spark plug or nozzle;
26 - supercharger;
27 - channel for supplying gas from the supercharger to the cavities 13 and 14;
28 - engine crankshaft (piston movement mechanism);
29 - crank left;
30 - crank right;
31 - connecting rods;
32 - rods connecting the pairs of pistons;
33 - oil-filled crankcase of the movement mechanism;
34 is a dividing wall.

 In FIG. 13 shows a two-row engine according to claim 8 in version 2, having at least two adjacent interconnected pairs of pistons moving in one direction, each of which has two pistons connected by a rod and connected to its crank. The cranks of each two adjacent pairs of pistons have a deviation between themselves in terms of the angle of rotation of the shaft and provide an advance opening and closing of the exhaust windows of the cylinder 7 with respect to the inlet windows of the cylinder 8.

 The principle of operation of a two-row multi-cylinder engine with an even number of adjacent pairs of pistons (more than two) will not differ from a two-row engine having two interconnected adjacent pairs of pistons, and therefore, an engine with two pairs of pistons is proposed for consideration.

 On Fig shows a variant of execution 2, when all the cylinders are working, their pistons move in one direction, and the purge of all the cavities of the cylinders is carried out from an external source, such as a supercharger.

 In the engine of FIG. 13, in the first row is a double-acting single acting cylinder 1, consisting of two cylinders 1 and two pistons 2.

 A cavity 3 is formed above the left piston 2, and a cavity 4 is formed above the right piston 2. The cavities 3 and 4 are interconnected by a channel 22. The cylinders 1 connected to each other have a common combustion chamber and can be considered as one twin cylinder. The double cylinder 1 has an inlet window 5 and an outlet window 6. Double-acting cylinders 7 and 8 are installed over the cylinder 1 through the dividing wall 34, having pistons 9 and 10, respectively. The pistons 9 and 10 of the second row are connected by rods 32 to the pistons 2 of the first row. Cavities 11 and 13 are formed above the pistons 9 and 10. Cavities 12 and 14 are formed under the pistons 9 and 10. All cylinders 1, 7 and 8 and all cavities 3, 4, 11 and 13 are working. A blower 26 is used to purge and pressurize all the cavities of the working cylinders. The working cylinder of the cavity 13 has inlet windows 17 and exhaust windows 18. The working cylinder of the cavity 11 has inlet windows 15 and exhaust windows 16. The cavities 12 and 14 are connected by a channel 24 and form a double cylinder. This twin cylinder has inlet windows 19 and outlet windows 20. The cavity 4 is connected to the cavity 13 bypass channel 21, and the cavity 3 is connected to the cavity 11 bypass channel 23.

 As a result, the cavities 13, 4, 3, and 11 communicate with each other and have a common combustion chamber, and the working cylinders of these cavities form a total cylinder consisting of 4 cylinders. While the cavity 4 and 3 are flowing and are located between the cavities 13 and 11, which are in the second row on the other side of the partition 34.

 A twin cylinder, consisting of 2 cavities 12 and 14 and a total cylinder, consisting of 4 cavities 13, 4, 3 and 11 each have their own spark plug or nozzle for fuel injection 25.

 A distinctive feature of the engine according to claim 8 of the claims of execution 2 in comparison with the closest prototype (I), as well as according to version 1, is that part of the working cylinders is not double, and the total cylinder has more than 2 cylinders. In the considered case of execution 2, the total cylinder consists of 4 cylinders.

 In this case, the cavities 3 and 4 of the working double cylinder of the first row are flowing, and for the double cylinder of the first row, the inlet windows 5 and the outlet windows 6 are located in the upper part of the cylinders and are not blocked by the piston. This arrangement of the windows of the first row cylinders, in contrast to the prototype, gives the advantages noted earlier.

 The principle of operation of the engine in version 2 is as follows.

 In FIG. 13, the moment is recorded when both interconnected pairs of pistons approach the BDC, and the working process ends in cavities 11, 3, 4 and 13, since the combustion of gases from these cavities takes place through exhaust ports 16, which opened earlier than the intake windows 17.

 Then, the closing of the outlet windows 16 and the opening of the inlet windows 17 begins. At this point, the cavities 13, 4, 3 and 11 are sequentially purged. After the outlet windows 16 are closed, the inlet ports 17 remain open and filling of the cavities 13, 4, 3 and 11 begins. gas with excess pressure that the supercharger can create. As a result, weight filling of the cylinder cavities can occur with a filling coefficient greater than unity. At the same time, the compression of the gas in the cavities 12 and 14 located under the pistons 9 and 10 ends. When the pistons approach the BDC, the mixture ignites, the gas expands and the pistons move up to the TDC, and therefore, the gas compression process in the cavities 13, 4, 3 and 11. When the pistons approach TDC, the exhaust ports 20 first open and burnt gases are released from the cavities 12 and 14.

At the beginning of the closing of the windows 20 and the beginning of the opening of the windows 19, the cavities 12 and 14 are purged. After the closing of the windows 20, filling of the cavities 12 and 14 begins with the open windows 19 with an overpressure equal to the pressure created by the supercharger. When the pistons approach TDC, the mixture ignites in cavities 13, 4, 3, and 11, the pistons move down to the BDC, and the process repeats. Those. for one revolution of the motor shaft there are two piston strokes with an interval of 180 ^{o the} angle of rotation of the shaft.

Execution 3, Fig.14
1 - a double working cylinder of unilateral action of the first row;
2 - pistons of cylinder 1;
3 - cylinder cavity 1 left;
4 - the cavity of the cylinder 1 is right;
5 - inlet window of cylinder 1;
6 - exhaust window of cylinder 1;
7 - left-sided cylinder of the second row;
8 - double-acting cylinder of the second row, right;
9 - the piston of the cylinder 7;
10 - the piston of the cylinder 8;
11 - the cavity of the working cylinder 7 above the piston;
12 - the cavity of the pump cylinder 7 under the piston;
13 - the cavity of the working cylinder 8 above the piston;
14 - the cavity of the pump cylinder 8 under the piston;
15 - the inlet window of the cavity 11;
16 - the outlet window of the cavity 11;
17 - the inlet window of the cavity 13;
18 - the outlet window of the cavity 13;
19 - inlet and outlet windows of the cavities 12 and 14;
20 - channel for supplying and discharging gas from cavities 12 and 14;
21 - supercharger;
22 - channel for supplying gas from the supercharger 21 to the cavity 13 of the working cylinder and to the pump cavities 12 and 14 of the pump twin cylinder;
23 - check valve;
24 - a bypass channel connecting the cavity 13 with the cavity 4;
25 - channel connecting the cavity 4 with the cavity 3;
26 - bypass channel connecting the cavity 3 with the cavity 11;
27 - channel connecting the cavity 12 and 14;
28 - spark plug or nozzle;
29 - engine crankshaft (piston movement mechanism);
30 - crank left;
31 - crank right;
32 - connecting rods;
33 - rods connecting the piston pairs;
34 - oil filled crankcase movement mechanism.

 In FIG. 14 shows a two-row engine according to claim 8 in version 3, in which four cavities, including two above the pistons of the first row and two above the pistons of the second row, are interconnected and are working. The principle of their operation is the same as that of the engine in execution 2 in FIG. 13. The difference from version 2 is that the cavities 12 and 14 of the twin cylinder are pumping and supply gas through the bypass channel 20 through the inlet window 17 to the working cylinders. With this design, the engine can have two operating modes - the starting mode with reduced power with the idle supercharger 21 and the operating mode with full power after turning on the supercharger. In this case, the total engine power will be less than that of the engine in version 2, because instead of six working cavities, only four working cavities will participate in the work, and two of the six cavities work only as pump cavities. On Fig considered an engine having only 2 pairs of pistons. With the same principle of operation, there can be a multi-cylinder engine having an even number of pairs of pistons connected by a rod.

 In FIG. 14, the moment is recorded when both interconnected pairs of pistons approach the BDC, and the work process ends in cavities 3, 4, 11 and 13 located above the pistons. In this position of the pistons from these cavities through the window 16, the release of burnt gases occurs, and in the pump cavities 12 and 14 the gas compression process ends, because check valve 23 is closed. When opening the window 17, first the process of purging the working cylinders begins, and then after closing the window 16, the working cavities are filled with fresh gas. After the window 17 is closed and the pistons start moving upward to the TDC, gas is compressed in the cavities 3, 4, 11 and 13 and at the same time, when the check valve 23 is open, filling of the pump cavities 12 and 14 starts. When the pistons approach the TDC, the fuel mixture ignites, the gas expands and the piston stroke begins.

 When the pistons move down, the check valve 23 closes and the gas is compressed in the pump cavities 12 and 14. The piston stroke ends when the window 16 opens and the burnt gases are released. After opening the window 17, the compressed gas from the pump cavities 12 and 14 expands through the bypass channel 20 and the window 17 enters the working cavity.

 After the pressure drop in the bypass channel 20, the check valve 26 opens and additionally through the channel 22 the gas through the window 17 begins to flow from the supercharger 21, which provides filling of the cavities 13, 4, 3 and 11 with excess pressure. When the supercharger 21 is inactive (engine starting mode), gas enters the working cavities only from pump cavities 12 and 14.

 When the supercharger 21 is operating, the non-return valve 23 is open and the cavities 12 and 14 can be filled with excess pressure. In this case, the engine will develop full power. When the supercharger 21 is idle, the cavities 12 and 14 will fill with gas without excess pressure and, accordingly, the engine will operate at reduced power. In the presence of pump cavities, it is easier to start the engine when the supercharger is idle, which can work from the energy of the exhaust gases as a turbocharger and only comes into operation after the engine is started when the estimated speed is reached. The presence of pump cavities allows the engine to operate without a supercharger at all.

The foregoing summary of claim 8 according to claim 4 is illustrated in FIG. 15, which has the following positions:
1 - working cylinder left of the first row;
2 - pump cylinder right of the first row;
3 - the piston of cylinder 1;
4 - the piston of the cylinder 2;
5 - the cavity of the working cylinder 1;
6 - cavity of the pump cylinder 2;
7 - the inlet window of the cavity 5;
8 - the outlet window of the cavity 5;
9 - the inlet window of the cavity 6;
10 - the outlet window of the cavity 6;
11 - dividing wall;
12 - a cylinder of double-acting second row left;
13 - double-acting cylinder of the second row, right;
14 - the piston of the cylinder 12;
15 - the piston of the cylinder 13;
16 - the cavity of the working cylinder 12 above the piston;
17 - the cavity of the pump cylinder 12 under the piston;
18 - the cavity of the pump cylinder 13 above the piston;
19 - the cavity of the working cylinder 13 under the piston;
20 - the inlet window of the cavity 16;
21 - the outlet window of the cavity 16;
22 - the inlet window of the cavity 17;
23 - the outlet window of the cavity 17;
24 - the inlet window of the cavity 18;
25 - the outlet window of the cavity 18;
26 - the inlet window of the cavity 19;
27 - the outlet window of the cavity 19;
28 - channel connecting the cavity 6 and 17;
29 - bypass channel connecting the cavity 5 and 16;
30 - bypass channel connecting the cavity 5 and 19;
31 - bypass channel connecting the cavity 17 and 19;
32 - bypass channel connecting the cavity 18 and 19;
33 - bypass channel connecting the cavity 6 and 19;
34 - engine crankshaft (piston movement mechanism);
35 - crank left;
36 - crank right;
37 - rod connecting the left pair of pistons;
38 - rod connecting the right pair of pistons;
39 - spark plug or nozzle;
40 - connecting rods;
41 - oil-filled crankcase of the mechanism of movement of the pistons.

In FIG. 15 shows a two-row engine in version 4, containing an even number of pistons connected by a rod, in which half of the cylinders are working and the other half of the cylinders are pumping. For convenience, see FIG. 15 shows a two-row engine having four pairs of pistons connected by a rod, of which every two pairs of pistons work independently and provide a predetermined push-pull cycle. The engine can be multi-cylinder with an even number of pairs of pistons. The presence of four pairs of pistons in the engine allows us to consider the full two-stroke cycle of two pairs of pistons in the range from 0 ^o to 360 ^{o the} angle of rotation of the shaft, because after every 180 ^{o the} position of the pistons with respect to TDC and BDC changes and one can see the start of the stroke for one pair of pistons, and the start of the compression cycle for the other pair of pistons.

In FIG. 15 shows the stage of the working cycle when the pistons 3 and 14 of the left pair of pistons approach the TDC, and the pistons 4 and 15 of the right pair of pistons approach the TMT. After 180 ^{o the} angle of rotation of the shaft, the pistons of the left and right pairs of pistons will change places. Because two pairs of pistons on the left side of the engine are the same as two pairs of pistons on the right side of the engine, the position designation of their constituent elements will be the same.

 In the engine of FIG. 15 in the first row are single-acting cylinders 1 and 2, and in the second row, cylinders 12 and 13 are double-acting cylinders. Above the piston 3 of the first row and above the piston 14 of the second row, as well as under the piston 15 of the second row, cavities 5, 16 and 19 of the working cylinders are formed, which have inlet and outlet windows, are interconnected, have a common combustion chamber, a common spark plug or nozzle for fuel injection and fire simultaneously.

 Over the piston 15 of the second row and over the piston 4 of the first row, as well as under the piston 14 of the second row, cavities 18, 6 and 17 of the pump cylinders are formed.

 The working cylinder of the cavity 19 has inlet windows 26 and outlet windows 27. The working cylinder of the cavity 5 has inlet windows 7 and outlet windows 8. The working cylinder of the cavity 16 has inlet 20 and outlet windows 21. The pump cylinder of the cavity 18 has inlet windows 24 and outlet windows 25 The pump cylinder of the cavity 17 has inlet windows 22 and exhaust ports 23. The pump cylinder of the cavity 6 has inlet windows 9 and exhaust windows 10. The pump cylinder of the cavity 17 is connected to the working cylinder of the cavity 19 bypass channel 31. The pump cylinder of the cavity 18 is connected to the working cylinder cavities 19 bypass channel 32. The working cylinder of the cavity 19 is connected to the working cylinder of the cavity 5 bypass channel 30, and the working cylinder of the cavity 5 is connected to the working cylinder of the cavity 16 bypass channel 29. In this case, the cavity 5 of the working cylinder of the first row is flowing and is located between the cavities 19 and 16, which are from the cavity 5 on the other side of the partition 11. As a result, the working cylinders of the cavities 5, 16 and 19 are built. Constructed working cylinders have a common combustion chamber, a common spark plug or nozzle for fuel injection 39.

 A distinctive feature of the internal combustion engine in embodiment 4 compared to the closest prototype (1) is that the working cylinders participating in the work are not double, like the prototype, but built. In this case, the cavities of the working cylinders of the first row are flowing, and their inlet and outlet windows are located in the upper part of the cylinders and do not overlap with the piston. The cavities of the pumping cylinders of the first row are also flowing, and their inlet and outlet windows are also located in the upper part of the cylinders.

 The location of the inlet and outlet windows of the cavities of the working and pump cylinders in the upper part of the cylinder gives the advantages noted in version 1, 2 and 3. In contrast to version 1 in version 4, a non-external blowing source is used to purge the working cylinders, for example in the form supercharger, and pump cylinders.

 The principle of operation of the engine in embodiment 4 is as follows.

 In FIG. 15, the moment is recorded when the working stroke of the pistons 15, 3, and 14 is completed in the right half of the engine in a built-up working cylinder containing interconnected cavities 19, 5, and 16. Accordingly, the release of burnt gases through the windows 21 ends at the same time or with a delay windows 26, and from the pump cavities 6, 17 and 18, the gas enters first into the cavity 19, then into the cavity 5 and then into the cavity 16. That is, sequential direct-flow purging of cavities 19, 5 and 16 takes place.

If the cranks of two interacting adjacent pairs have a deviation between themselves in the angle of rotation of the shaft by 180 + α ^° , the opening and closing of the outlet windows 21 is ahead of the inlet windows 26.

This allows you to improve the fill factor of the working cylinder. A variant is possible when a supercharger will be used to fill the pump cylinders, creating a pressure above atmospheric. In this case, in the working cylinder after closing the exhaust ports 21, the pressure can also be raised above atmospheric. At the same time, in the left half of the engine (two pairs of pistons on the left), the fuel mixture ignites above the pistons 14 and 3 and under the piston 15. The gas expands and the pistons travel in a cylinder with interconnected cavities 19, 5 and 16. As a result, the pistons 14 and 3 move to the BDC, and the piston 15 moves to the TDC. First, windows 21 open, and the discharge of burnt gases occurs. Then the windows 26 begin to open, and the cavities 19, 5 and 16 are purged and then filled. By this time, pistons 14, and 3 in the right half of the engine (two pairs of pistons on the right) approached the TDC, and piston 15 approached the BDC. It ignites and the pistons move in the right half of the engine. Then the work cycle is repeated. As a result, in the engine under consideration, for one revolution of the shaft, two trips of the built working cylinders occur with an interval of 180 ^o .

Sources of information
1. Two-stroke internal combustion engine (options). RF patent 2143077, IPC F 02 B 33/22, publ. 1999, Bull. 35.

 2. A.K. Mikhailov, V.P. Voroshilov. Compressor machines: Textbook for high schools - M .: Energoizdat, 1989, p. 11, Fig. 1, 2, 6 and 7).

Claims (8)

 1. A piston machine, for example, as a two-stroke or four-stroke internal combustion engine, a compressor for compressing or sucking gas or a pump for pumping a liquid medium, containing cylinders with cavities in which pistons, an inlet chamber and an exhaust chamber in which cylindrical spools rotate, connected to the engine shaft, and inlet and outlet windows connected bypass channels to the intake and exhaust chambers, characterized in that it contains at least two cylinders, the inlet chamber is located above one cylinder, and exhaust - on the other, with each camera working on two cylinders.  2. The piston machine according to claim 1, characterized in that the cylinder cavities are interconnected by means of a channel with the formation of a common combustion chamber for two cylinders, and the pistons move in one direction, while one cylinder has inlet windows and the other cylinder outlet windows.  3. The piston machine according to claim 1, characterized in that the cylinders operate independently of each other, the pistons of the cylinders counter-move and work in antiphase, two spools are placed in the intake and exhaust chambers, and each cylinder has an inlet and an outlet window.  4. A piston machine containing at least two adjacent working cylinders with working cavities in which pistons are connected, each connected with its crank, inlet chambers and exhaust chambers, in which the spools connected with the pistons, inlet and outlet windows made in the workers are moved cylinders above the pistons at their position at top dead center and connected by bypass channels with the windows of the inlet chamber and the exhaust chamber, characterized in that the spools are connected to the pistons using rods, and the chambers are mounted above the working pistons through the separation partition.  5. The piston machine according to claim 4, characterized in that the working cavities are interconnected by a channel with the formation of a common combustion chamber for two working cylinders, the pistons move in one direction, with one cylinder having inlet windows and the other cylinder outlet windows.  6. The piston machine according to claim 4, characterized in that the cylinders are independent, the working pistons counter-move and work in antiphase, with each cylinder having inlet and outlet windows.  7. Piston machine according to any one of paragraphs. 4-6, characterized in that the spools are made of rectangular cross-section.  8. A piston machine containing cylinders located through a partition wall one above the other, in which the pistons of the cylinders of the first row are connected by rods to the pistons of the cylinders of the second row, and the working cylinder is doubled and has inlet and outlet windows and a common combustion chamber communicating its working cavities which are located on both sides of the partition, characterized in that the working cavities of the cylinders of the first row are flow-through and connected from the side of the gas inlet and outlet with the working cavities of the cylinders of the second row, and in the inlet and outlet windows of the cylinders of the first row are made in the upper part of the cylinder above the piston at its position at top dead center.

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