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INVENTION
Patent of the Russian Federation RU2285125
ROTARY INTERNAL COMBUSTION ENGINE
Applicant's name: Oleg Georgievich Chanturia (RU); Chanturia Igor Georgievich (UA)
The name of the inventor: Chanturia Oleg Georgievich (RU); Chanturia Igor Georgievich (UA)
The name of the patent holder: Chanturia Oleg Georgievich (RU); Chanturia Igor Georgievich (UA)
Address for correspondence: 183693, Murmansk, ul. Papanin, 4, GU "Murmansk TsNTI", Patent Department, LL Kirjanovoy
Date of commencement of the patent: 2004.12.03
The invention can be used as a power plant of various machines, including as an ICE of vehicles. The rotary internal combustion engine contains a fixed body with grooves formed thereon, rigidly mounted on the rotor shaft, in the body of which there are 2 n pairs of blades, each pair of blades is two plates parallel to the rotor body, the combustion chambers formed between the plates of each Pairs of blades, and retractable devices. Plates are made in the form of working and auxiliary, successively extended, consisting of two parts of different thicknesses. On the parts of thicker plates moving along the rails inside the rotor, there are gear racks and pushers for mating with a pull-out device, which for each pair of blades is a rack and pinion-pinion-crank mechanism incorporating a slider with a rack, In gearing with the gear-cam shaft, on which two incomplete gear wheels, damped relative to each other, with the accelerating-brake cams, are placed on both sides of the central gear. On the rim of the rotor between the plates of each pair of blades are made grooves, forming with the plates of the combustion chamber. The profile of the grooves of the body in cross section is a part of two unipolar n-period antiphase sinusoids displaced by an angle corresponding to the distance between the blades, reduced to a circle, with n = 1, 2, 3 ... The motor is compact, simple in construction, reliable In operation, has a high specific power.
DESCRIPTION OF THE INVENTION
The invention can be used as a power plant of various machines, including as an ICE of vehicles.
There are known engines with a rotating cylinder block, in particular an engine according to RU 2213235 C2, 27.09.2003, F 02 B 57/08 (analog) . The engine comprises a fixed body, a rotor, a rotating cylinder block with pistons and a gear-and-crank mechanism, through which the pistons move radially.
This engine is compact, but the gear-crank-and-crank mechanism in it is power, which leads to power losses due to friction and inertial loads.
The closest to the claimed is a two-stroke rotary internal combustion engine according to RU 37389 U1, 20.04.2004, F 02 B 53/00 (prototype) . The engine comprises a fixed housing with grooves formed therein, a rotor rigidly mounted to the shaft, and retractable and locking devices. The grooves of the body with the rim of the rotor form successively located alternating functional cavities. In the body of the rotor there are slider blades that move along the guides in the guide rails and are frames with retractable side walls, the cavities between which, with built-in spark plugs, form combustion chambers.
Disadvantages of this engine are insufficient reliability due to the possible mismatch of the work of the sliding and locking devices, the complexity of the lubrication and cooling processes of the engine.
The problem solved by this invention is to create and improve the design of a powerful, economical and compact engine.
The technical result of the invention is to reduce the overall dimensions of the engine, increase the reliability of its operation, increase its power and increase the efficiency of energy use of gases and, accordingly, the efficiency of the engine.
This task is achieved by the fact that in a rotary internal combustion engine containing a fixed body with grooves formed therein, a rotor rigidly mounted on the shaft, in the body of which there are 2 n pairs of blades, each pair of blades is two plates parallel to the rotor body , The combustion chambers formed between the plates of each pair of blades and the pull-out devices according to the invention are made in the form of a working and auxiliary, successively extending, consisting of two parts of different thickness, on the parts of plates of greater thickness, moving along the guides inside the rotor, Racks and pushers to interface with a retractable device, which for each pair of blades is a rack and pinion-pinion-crank mechanism, including a slider with a rack, engaged with a gear cam shaft, which is densely planted on both To the sides of the central gear, two incomplete gears offset from each other, with acceleration-brake cams, on the rim of the rotor between the plates of each pair of blades, grooves are formed, forming with the plates of the combustion chamber, the profile of the grooves of the body in cross section is the parts of two unipolar n -periodic antiphase sinusoids displaced by an angle corresponding to the distance between the blades, reduced to a circle, with n = 1, 2, 3 ...
The same task is achieved when the auxiliary plate of each pair of blades and the slider of the withdrawable device are in the form of one piece, while the gear-cam shaft is arranged horizontally or vertically in the windows made on a part of the plates of greater thickness.
The execution of plates in the form of working and auxiliary, successively extended, consisting of two parts of different thickness, the execution on the parts of plates of greater thickness, moving along the guides inside the rotor, gear racks and pushers for coupling with the withdrawable device increases the reliability of the engine by simplifying the design of power components Rotor and due to the smaller thickness of the pair of blades, it makes it easier and more reliable to provide compression in the functional cavities, provides an increase in power due to the fact that 2 rotations of force are generated per rotor revolution. The force vector is applied to the blades and is directed along the tangent to the rotor, which increases the specific power of the engine, its torque, increases the efficiency of gas energy use and, accordingly, the efficiency due to the larger arm of force application. The arrangement of the operating elements in the rotor body reduces the overall dimensions of the motor.
Execution of a pull-out device for each pair of blades in the form of a rack and pinion-pinion-crank mechanism incorporating a slider with a rack, engaged in a gear-cam shaft, on which two incomplete gear teeth are placed on each side of the central gear Wheels displaced with respect to each other, with acceleration-brake cams, provides an increase in the reliability of the engine by placing the device in the body of the rotor, performing the functions of the locking device by the elements of the withdrawable device, which eliminates the mismatch of the engine parts, provides a different amount of extension of working and auxiliary Blades from the body of the rotor, that is, the creation of different in terms of volume of working and auxiliary cavities, which, in turn, increases the efficiency of gas energy use and engine efficiency. This design of retractable devices provides high engine power due to an insignificant power take-off by pull-out devices and a reduction in the overall dimensions of the engine due to a slight displacement of the slide in the body of the rotor.
The execution on the rim of the rotor between each pair of vane blades forming together with the blades of the combustion chamber increases the reliability of the engine due to the simplicity of the design, allows for simplification of cooling and lubrication and enables the use of standard spark plugs or nozzles with their traditional arrangement in a stationary body.
The grooves formed in the housing with a profile representing in cross section a part of two unipolar n-period antiphase sinusoids displaced by an angle corresponding to the distance between the blades, reduced to a circumference, with n = 1, 2, 3 ... , which with a rim Rotor form successively located alternating functional cavities with inlet and outlet windows, provide an increase in engine power, allow more precise adjustment of the ratio of fuel and air in the working mixture, which eliminates the need for turbocharging.
The implementation of the auxiliary plate of each pair of blades and slider of the pull-out device in the form of one piece, the arrangement of the gear-cam shaft in horizontal or vertical direction in the windows made on a part of the plates of greater thickness, and reduces the overall dimensions of the engine and increases the reliability of its operation due to the simplification of its design while maintaining Power and efficiency of the engine.
Thus, the aforementioned set of features of the invention makes it possible to provide a new technical result: reducing the overall dimensions of the engine, increasing the reliability of its operation, increasing its power and increasing the efficiency of using gas energy and, accordingly, the efficiency of the engine.
The invention is explained with the aid of the drawings, in which: FIG. 1 is a perspective view of a push-pull rotor engine; FIG. 2 shows a general view of the rotor, FIG. 3 shows a cut-out A in FIG. 2 , FIG. 4 shows a general view of the gear camshaft , FIG. 5 shows a general view of the gear cam wheel, FIG. 6 shows a general view of the gear cam wheel in a stationary state, FIG. 7 shows a general view of the gear cam wheel during acceleration and extension of the auxiliary blade, FIG. 8 - a general view of the gear-cam wheel when the auxiliary blade is braking; Fig. 9 is a perspective view of a drawer, the slider of which with the auxiliary blade is made in one piece with the vertical arrangement of the gear-cam shaft; And two auxiliary cavities, FIG. 11 is a diagram of the operation of the engine in the initial position, FIG. 12 is a diagram of the operation of the engine at the moment of ignition of the compressed working mixture.
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The two-stroke rotary internal combustion engine ( see FIG. 1 ) consists of a stationary body 1, 2, a rotor 3 rigidly mounted on the shaft 4, n pairs of blades 5 (four in this embodiment) and retractable devices 6. The body consists of two parts : Main 1 and upper 2. The main part is a hollow cylinder (drum) having a bottom where the lower support 7 of the shafts of the motor shaft 4 is located. The outer side of the support 7 has a cylindrical gear ring 8 for driving the pull-out devices 6. On the inner rim of the main body part 1, grooves 9 are formed with a width equal to the height to which the blades 5 are projected from the body of the rotor 3. The groove profile 9 in cross- Unipolar n-period antiphase sinusoids offset by an angle corresponding to the distance between the blades, reduced to the circumference, where n = 1, 2, 3 ... Thus, the grooves 9 with the rotor rim 3 form n / 2 working 10 and n / 2 auxiliary 11 alternating cavities. On the rim walls of the main body part 1 at the beginning of the auxiliary cavities 11 there are inlet windows 12 and at the end of the working cavities 10 the outlet windows 13. In the transitions between the auxiliary cavities 11 and the working cavities 10 on the body 1, threaded holes 14 for the spark plugs 15 are provided. Ignition 15 can be several. In the upper part 2 of the housing there is an upper support of the pins 16 of the motor shaft 4. |
The rotor 3 ( see FIG. 2 ) is a cylindrical body in which four pairs of blades 5 and extenders 6 are disposed. On the rim of the rotor 3 holes 17 are provided for the exit of pairs of blades 5. Each pair of blades 5 consists of a working 18 and Auxiliary blade 19, each of which extends only into its functional cavity: the working blade 18 into the working cavity 10, the auxiliary blade 19 into the auxiliary cavity 11. The blades 18 and 19 are plates consisting of two parts: the first part of a smaller thickness directly A blade (a solid plate extending from the body of the rotor 3 into the functional cavities 10, 11) and a second part of a larger thickness with a window 20 and a notch 21 for positioning and functioning of the elements of the withdrawable device 6. The first part of the working blade 18 is made thicker than the first part Of the auxiliary blade 19. The second portions of the larger thickness blades 18, 19 move along the guides 22 inside the rotor 3. |
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On the inner sides of the windows 20, the rack bars 23 and 24 are engaged in engagement with the elements of the slide device 6. The toothed rails 23 and 24 are formed on different sides of the windows 20. In this embodiment of the engine, the rack 24 is formed on the upper part of the window of the blade 16, The rack 23 is formed on the lower part of the window of the auxiliary blade 19. The working blade 18 and the auxiliary blade 19 have pushers 25 for interfacing with the elements of the withdrawing device 6. The blades 18 and 19 are designed to implement in the engine the energy conversion of gases into mechanical motion (working blades 18 ) And compression of the working mixture (auxiliary vanes 19). The engine can have 2n pairs of blades. In the body of the rotor 3, grooves 26 are formed, forming with the combustion chamber blades 18, 19. | |
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The pull-out device 6 provides alternate extension of the blades 18, 19, returning them back and fixing them in accordance with the strokes of the engine. The withdrawable devices 6 in the rotor are as many as the pairs of blades 5. The withdrawable device ( see FIG. 3 ) is a rack and pinion-pinion-crank mechanism and consists of a toothed wheel 27 of a crank 28, a connecting rod 29, a slider 30 and a gear- Cam shaft 31. The slider 30 is a plate with a window 32 at the bottom of which a rack 33 is formed that engages the central gear 34 of the gear-cam shaft 31. The slider is fixed and moves along the guides 35 formed in the body of the rotor 3. The gear-cam shaft 31 Is made with a central gear 34, two gear-and-cam wheels 36 and 37, which are two incomplete gears with acceleration-brake cams engaged with the rack bars 23 and 24 of the blades 18 and 19 and in conjunction with the pushers 25. The gear-cam The shaft 6 is located in the windows 32 and 20 of the slider 30 and the blades 18, 19 perpendicularly to the plane of their plates and is mounted in vertical struts 38 ( FIG. 3 shows a fragment of the column 38, entirely in FIG. 1 ). |
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The gear-cam wheels 36, 37 ( see Fig. 4 ) are two incomplete gears 36 and 37 with their respective acceleration-braking cams 39. The gear-cam wheels 36, 37 are disposed on the shaft 31 with an angular displacement relative to each other, Which provides a sequence of extension of the working 18 and auxiliary 19 blades. The incomplete gear 37 (as well as 36) includes four sectors ( see FIG. 5 ): sector I, the arc of which is made with a ring gear, sector II, whose arc is made with a variable radius vector, sector III with an arc of constant radius Greater than the radius of the normal line of the ring gear, and sector IV with a constant radius smaller than the radius of sector III. The acceleration and deceleration cam 39 and consists of sectors: a sector V with a variable radius vector and a sector VI with an arc of constant radius. The gears 36, 37 at a certain moment engage with the racks 23, 24 of the blades 18 and 19, providing them with a discontinuous movement. The acceleration and brake cams 39 are located only in the plane of action of the pushers 25 of the blades 18, 19. The working profile of the sector II of the wheel 37 and the sector V of the acceleration brake cam 39 is made with the same curvature in accordance with the law of motion of the blades 18, 19. In order to ensure shock The distance H between the contact point of the pusher 25 and the tooth of the rail 23 and the chord distance h on the sectors of the sectors of the wheel 37 and the acceleration brake cam 39 simultaneously entering into contact with the working surfaces of the blade 19 are equal to each other. | |
The gear ratio is
Where R z.v.o. - radius of the ring gear 8 of the support 7 of the shafts of the motor shaft,
R z.k. Is the radius of the toothed wheel 27 of the crank 28.
The ratio of the radius of the normal line of the central gear 34 to the radius of the normal arc line of the gear ring of the gear cam wheels 36 and 37 determines transmission factors K:
Where R cms. Is the radius of the normal line of the central gear 34,
R s.v.1 - radius of the normal line of the gear ring of the gear-cam wheel 36 (working)
K 1 is the transmission coefficient of the impeller 36.
Where К з.в.2 - radius of a normal line of a gear of a gear wheel gear-cam wheel 37 (auxiliary),
K 2 - transmission coefficient of the auxiliary wheel 37.
The transmission coefficients K 1 and K 2 show the multiplicity of the extension of the blades 18, 19 relative to the displacement of the slider 30. K 1 and K 2 may be equal to each other, but may be different in magnitude. Structurally changing K 1 and K 2 with a slight displacement of the slider 30, we obtain the necessary extension of the blades 18, 19. For different values of K 1 and K 2, the amount of extension of the working 18 and auxiliary blades 19 with respect to each other varies, forming at the same time different working volumes 10 and an auxiliary cavity 11.
The extension of the blades 18, 19 occurs when the sector I with the gear rim of the corresponding gear 36, 37 with the rack 23, 24 of the vanes 18, 19 comes in. For additional braking of the blades 18, 19, the plate springs 40 are provided in the body of the rotor 3.
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The movement of the blades 18, 19 is carried out as follows. In the stationary state ( see Fig. 6 ), the blade 19 is fixed by conjugating the contact points of the pusher 25 and the nape of the first tooth of the rail 24 to the working surfaces of the sector VI of the accelerating cam 39 and the sector III of the incomplete gear 37 made with an arc of constant radius. Acceleration and extension of the blade 19 ( see Fig. 7 ) is carried out by running-in on the contact surface of the pusher 25 of the sector V of the acceleration-brake cam 39 and when the working surface of the sector II of the incomplete gear 37 is pushed over the nape of the first tooth of the rail 24 to the gear of the sector I The wheels 37 with the rack gear 24 of the blade 19. The braking of the blade 19 ( see Fig. 8 ) occurs as follows: with the still existing gear of the sector gear I of the wheel 37 with the rack bar 24, the pusher 39 comes into contact with the working surface of the acceleration- Cam 39, which, when rotating, extinguishes the kinetic energy of the blade 19. In the braking of the blade 19, the plate springs 40 also take part.
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Preferably, the radial arrangement of the blades 5 with the pulling device 6 is not radial, and the chordal (not shown in the figure) away from the shaft 4 in the rotational direction of the rotor 3. This results in an even smaller reduction in the overall dimensions of the rotor 3, and therefore of the motor. With a slight extension of the working blades 18, an additional torque arises due to the pressure of the gases on the rear wall of the combustion chamber formed by the inner faces of the blade plates 18, 19 and the arm equal to the displacement of the elements of the withdrawing device 6 from the axis of the shaft 4. The auxiliary blade 19 can be made as a single piece with the slide 41 of the slide device 6. Here, the gear-cam shaft 31 is formed with one gear-and-cam wheel 42 and a pinion 43 and can be arranged vertically between the blades 18 And 19. The toothed rails 44, 45 are formed on the inner sides of the blades 18, 19 at different levels. The gear rack 44 of the operating blade 18 engages the gear-cam wheel 42 and the rack bar 45 with the gear 43. The auxiliary blade 19 with the slide 41 is in this embodiment of the engine in continuous reciprocating motion. The blade 19, completely retracted into the body of the rotor 3, continues to move inside the rotor 3 by the crank rod 29 value. |
ENGINE WORKS AS FOLLOWING
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In the embodiments shown in these drawings, the engine is designed with four pairs of blades 5. Accordingly, the engine has two diametrically disposed ( see FIG. 10 ) working cavities 46 and 47 and two auxiliary cavities 48 and 49. The transition regions 50, 51 From the working cavities 46, 47 to the auxiliary 48, 49 smaller than the transition portions 52, 53 from the auxiliary cavities 48, 49 to the workers 46, 47 by the distance between the working blade 18 and the auxiliary blade 19 relative to each other. Functional cavities in this case are equal, K 1 = K 2 . At the beginning and at the end of the functional cavities 46-49, flat sections of acceleration 54 and braking 55 are made. In describing the operation of the engine, the operation of the drawers and blades described above is not considered. |
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Let the working mixture be in the initial state ( see Fig. 11, position I ) in the auxiliary cavity. The auxiliary blade 19 ( see Fig. 10, position II ) extends from the body of the rotor 3, compresses the working mixture with the front face and, sucking a new portion of the working mixture through the inlet window 12 into the auxiliary cavity 48 (gas-firing stroke), creates a vacuum. After the blades 18, 19 of the auxiliary cavity 48 pass through the transition 52 separating the auxiliary 48 and the working cavity 46 ( see Fig. 11, position III ), both vanes 18, 19 are in the body of the rotor 3 and are stationary. The working mixture is then compressed to the maximum in the combustion chamber 56 formed by the inner faces of the blade plates 18, 19 and the recess 26 in the body of the rotor 3. As the rotor 3 continues to move, the combustion chamber 56 is fed ( see FIG. 12, position IV ) The arrangement of the spark plugs 15 located in the engine casing 1 where, at the appropriate time, the spark of the spark plug 15 ignites the compressed working mixture.
Extending the working blade 18 ( see Fig. 10, position V ) with an internal face perceives the pressure of the gases, converts it into rotational motion of the rotor 3, pushing the remains of the exhaust gases of the previous working stroke out through its outlet window 13 (working stroke) with its outer edge. In this engine with 4 pairs of blades 5 concurrently there are processes corresponding to the working stroke for two pairs of diametrically located blades 5 and with a slight lag (advance) of the gas-firing stroke for the other two pairs of blades 5. Thus, the working stroke occurs for a half-turn of the engine.
The claimed rotary internal combustion engine is compact, simple in design, reliable in operation, has high specific power and efficiency.
CLAIM
The rotary internal combustion engine comprising a fixed body with grooves formed therein, rigidly mounted on the rotor shaft, in the body of which there are 2 n pairs of blades, each pair of blades is two plates parallel to the rotor body, the combustion chambers formed between the plates Each pair of blades, and sliding devices, characterized in that the plates are made in the form of a working and auxiliary, successively extended, consisting of two parts of different thickness, on the parts of plates of greater thickness, moving along the guides inside the rotor, gear racks and pushers for mating with A sliding device which for each pair of blades is a rack and pinion-gear-crank-connecting rod mechanism including a slider with a rack, engaged in a gear-cam shaft, on which two incomplete Gear wheels offset relative to each other with acceleration-brake cams, on the rim of the rotor between the plates of each pair of blades, grooves are formed that form with the plates of the combustion chamber, the profile of the grooves of the body in cross section is part of two unipolar n-period antiphase sinusoids offset At an angle corresponding to the distance between the blades, reduced to a circle, with n = 1, 2, 3 ....
The engine as claimed in claim 1, wherein the auxiliary plate of each pair of blades and the slide of the withdrawable device are made in one piece, the gear cam shaft being horizontal or vertical in the windows formed on a part of the plates of greater thickness.
print version
Date of publication 16.11.2006гг
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