RU2227219C2 - Opposite cycle rotary piston engine - Google Patents

Abstract

FIELD: mechanical engineering; internal combustion engines. SUBSTANCE: proposed engine consists of housing, single-throw shaft and rotor freely rotating on journal of crank in space of quadratic chamber. According to invention, housing of engine is made in form of two members of quadratic closed partitions getting one into the other and two end face covers closing the partitions and reducing them. Space formed by smaller closed partitions serves as working chambers and space between partitions serves as water cooling jacket. Combustion of compressed air- fuel mixture is performed in bypass tubular combustion chamber in water cooling jacket and closing delivery and working stroke valves pockets. EFFECT: improved efficiency of operation of rotary piston engine. 6 dwg

Description

The engine design refers to a complete set as the main drive mainly in automobile transport, as well as on other types of vehicles, and on equipment in industry for the extraction or processing of raw materials.

It is known that there is an analogue, the rotary piston engine 12A, created in 1957 by F. Wankel and the Mazda company with a capacity of 80 kW at 6000 rpm (Internal combustion engines: Design and operation of piston and carburetor engines / Ed. A. S. Orlina, M.G. Kruglova. - 3rd ed., Revised and revised - M .: Mashinostroenie, 1980.- 288 p.).

The following indicators can be attributed to the set of essential features of the analogue:

1. The design of the engine has a conditional horizontal arrangement of the shaft with two hollow rotors on its eccentrics, deployed relative to each other in parallel rotation planes of 180 °.

2. The engine casing consists of two epitrochoid elements and a spacer built between them, as well as two closing end caps that form two working chambers in parallel planes.

3. On the outer surfaces of the end caps of the housing and the ends of the shaft passing there, there are gearing devices with a gear ratio of 3: 2, which, in turn, provides a given planetary rotation of the rotors and rotation of the eccentrics with the transmission of torque to the power take-off shaft.

4. The planetary-translational rotation of the vertices of both rotors and the convex surfaces connecting them create conditions for the formation of segmented cavities in the working chambers with slightly distorted shapes and varying volumes, as well as their movement in the direction of rotation of the shaft.

5. In the study of the analogue, it was found that the inner surface of any one of the two working chambers is determined by the rotation of the rotor vertices in the XOY coordinate system according to the following formulas:

Xn = R · cos (αn + Z · 120 °) + r · cos (180 ° + βn);

Yn = R · sin (αn + Z · 120 °) + r · sin (180 ° + βn);

where Xn are the coordinates of the point on the abscissa;

Yn - coordinates of the point on the ordinate axis;

R = 5r is the distance from the center to the top of the rotor;

r is the center distance on the shaft eccentric;

αn is the angular displacement of the rotor;

βn = 3αn is the angular displacement of the crank;

Z is 0; 1; 2 - value for the vertices A, B, C;

n - set points.

6. The outer surface of the rotor in section AB is determined in the coordinate system X’O’U ’due to contact with a fixed point of the apex of the protrusion of the working chamber, lying at a distance F along the axis OX. As a result of the rotor rotation, it is possible to determine the coordinates of the points under study using the following formulas:

X’n = F-r · cos (180 ° + βn);

Y’n = -r · sin (180 ° + βn),

where X’n, Y’n are the coordinates of the given points;

F = 4 · r.

Formulas for constructing three rotor surfaces from the calculated points obtained are of the form

where Pn = (3-5) r is the limit of the value of the parameters of the points from the center to the surface of the rotor;

λn = 0-120 ° - section AB, Z = 0;

λn = 120-240 ° - section of the aircraft, Z = 1;

λn = 240-360 ° - area of CA, Z = 2.

7. The work of the gas distribution device is determined by the overlapping of the openings of the windows in the working chamber with the surfaces of the rotor for the inlet, bypass and outlet channels.

8. The combustion of the compressed air-fuel mixture is carried out in the cross-spacer channels of the spacer, which are cyclically connected with single-row halves of some working chambers with others, when exposed to electrical discharges on the built-in spark plugs. The combustion process in each cycle is accompanied by an increase in pressure in the combustion chamber with its transition to the working chamber, which ensures a working stroke.

9. In-line cyclic processes create an engine operating mode in the conditions of a 4-stroke 4-cylinder piston engine.

10. Improving the dynamic characteristics due to the lack of rotating masses of the analog engine will allow to increase the maximum speed on the main shaft when compared with conventional carburetor type piston engines.

11. The cooling system of the inner surfaces of the rotors, bearing elements and internal cavities of the working chambers is provided by a draft of cooling air. The cooling of the outer surfaces of the working chambers and combustion chambers in the spacer is provided by the water circulation cooling system.

The essential features of a rotary piston engine with opposed cycle processes include the following:

1. The engine design has a vertical shaft arrangement in the main body, where one freely rotating toroidal rotor is installed on the crank pin of the crank.

2. The design of the housing is made up of two elements of closed partitions of a quadratic type that enter one into the other, as well as two end caps that close them, which compress these partitions. The cavity formed by a small closed partition serves as a working chamber, and the cavity between the partitions serves as a water cooling jacket. In the central part of the axis of the covers there are through cylindrical sleeves for sliding bearings and adjacent through channels adjacent to them around the circumference for air cooling of the inner surfaces of the rotor and the working chamber, as well as for cooling the main shaft and its sliding bearings. The hollow parts of the covers serve to distribute and collect the coolant of the water jacket.

3. The operation of the proposed engine is provided by the reciprocal planetary rotation of the rotor in the quadratic cavity of the working chamber, which is conditionally divided into two parts of the grouping cyclic processes located opposite, ie 180 ° against each other. In this case, the planetary rotation of the rotor will be ensured by rolling over the rotor tops along the troughs of the inner surface of the working chamber, with a gear ratio of 3: 4.

4. The reciprocal rotation of the rotor in the cavity of the working chamber creates the conditions for the formation of highly distorted segment cavities with varying volumes, which have a movement in the direction opposite to the rotation of the motor shaft. In the bypass tubular combustion chambers, the movement of gas flows will be directed in the direction of rotation of the main shaft.

5. In the theoretical development of the proposed engine, it was found that the inner surface of the working chamber is determined by the rotation of the rotor vertices in the XOY coordinate system according to the following formulas:

Xn = R · cos (αn + Z · 120 °) + r · cos (180 ° -βn);

Yn = R · sin (αn + Z · 120 °) + r · sin (180 ° -βn);

where Xn are the coordinates of the point on the abscissa axis;

Yn - coordinates of the point on the ordinate axis;

R = 5r is the distance from the center to the top of the rotor;

r is the center distance on the shaft eccentric,

αn is the angular displacement of the rotor;

βn = 3αn is the angular displacement of the crank;

Z is 0; 1; 2 - values for the vertices A, B, C;

n is the number of the specified point.

6. The outer surface of the rotor is determined by the condition of predefined points in the first quadrant of the coordinate system X’O’Y ’for the upper half of the section AB by the formulas

X'k = r [19cos (γ _to : 13.664) -16 + 0.005sin (180 ° tg (1.4255k + 0.032k ² ))];

Y'k = r [19sin (γ _to : 13.664) + 0.6sinγ _to ],

where Х’к and Y’к - coordinates of the given points;

19 - coefficient of radial distance of the center of the construction;

γ _k is the specified construction angle from 0 to 180 °, which is determined from the condition γ _k = kΔγ, where k is the number of the given point and k is the value directly proportional to it 0-30, and Δγ is the step between two adjacent points of the initial radius and will be correspond to 6 °;

13.664 - concentration coefficient of the surface of the construction;

16 - compensation coefficient of the removal of the center of the construction.

We use the obtained values to construct the rotor surface through angular coordinates and radial distance

The coordinates of the second half of the rotor surface in the fourth quadrant for X'k remain the same, and for Y'k they will be oppositely negative for k = 0 - (- 30). To create formulas that determine the position of all given points of the surface of the rotor, taking into account its rotation in the working chamber, we introduce P _k and λ _k in the formulas of clause 5

X _nk = P _to cos (λ _to -α _n ) + r cosβ _n ;

Y _nк = Р _к sin (λ _к -α _n ) + r sinβ _n .

7. The work of the gas distribution device is provided by a system of eight lever-turn valves located in the pockets of the closed partition of the working chamber, which are driven by the action of a rotating three-jaw distribution disk mounted on the opposite end of the power take-off shaft.

8. The combustion of the compressed air-fuel mixture is carried out in two bypass tubular combustion chambers located in the water cooling jacket, the ends of which close the pockets of the discharge and working valves.

9. In the proposed RPD, the rotation of the rotor upon contact of its outer surface with the inner boundary of the cavity of the working chamber will form distorted cavities and determine the opposite location of the created processes with five cycles, which, in turn, will ensure the operation of the engine in the mode of a four-stroke five-cylinder piston engine.

10. Improved dynamic performance of this engine will allow a significant reduction in idle speed with a reduction in fuel consumption and a significant increase in speed in operating mode.

11. The engine cooling system will be similar, with the exception of a significant increase in the process of heat removal from the surfaces of the tubular combustion chambers.

12. The expected service life of the proposed engine when compared with the analog will be more than 2 times longer for the following reasons:

a) the lack of gear for rotation of the rotor;

b) a decrease in pressure on the end surfaces of the rotor by 2 times, because instead of two rotors, one is used;

c) reduction of sliding friction of the outer surfaces of the rotor along the inner surface of the working chamber;

d) the ability to reduce pressure by 2 times on radial sealing plates due to the absence of negative radial acceleration, creating conditions for their separation from the sliding surface;

d) reduced wear of the outer surfaces of the rotor, the inner and end surfaces of the working chamber, as well as mechanical and radial seals in connection with the above reasons by 2 times.

Figure 1 shows the planetary motion of the rotor vertices, which determine the trajectory of the inner surface of the working chamber in the coordinate system of the HOU with their common center. In this case, the angular movement of the crank is examined from 0 to 360 ° with an interval of 15 ° and is described by the following formulas:

Xn = R · cos (αn + Z · 120 °) + r · cos (180 ° -βn);

Yn = R · sin (αn + Z · 120 °) + r · sin (180 ° -βn),

where Xn are the coordinates of the point on the abscissa axis;

Yn - coordinates of the point on the ordinate axis;

R = 5r is the distance from the center to the top of the rotor;

r is the center distance of the center of the shaft and rotor;

αn is the angular displacement of the rotor;

βn = 3αn is the angular displacement of the crank;

Z is 0; 1; 2 - value for the vertices A, B, C;

n - set points.

Further movement of the vertices A, B, C along the studied points in all the following quarters will be similar.

Figure 2 shows the construction of the outer surface of the rotor between the vertices A and B in the coordinate system X’O’Y ’. In this case, we set the conditions

f _xy = f ' _xy + Δf' _xy ,

where f _x = f ' _x + Δf' _x , f _y = f ' _y + Δf'_y;

f ' _xy - defined function;

Δf ' _xy - increment to the specified function;

f ' _x = r [19cos (γ _c : 13.664) -16];

f _'y = r l9sin (γ _to: 13.664);

Δf ' _x = r 0.005sin (180 ° tg (1.4255k + 0.032k ² ));

Δf ' _y = r 0.6sinγ _k .

The obtained results were used to construct all three surfaces and verified during planetary rotation in the working chamber using the animation method on the computer screen using the TFLEX-CAD-2D program.

Figure 3 shows the animation of the processes of one full cycle in the opposed rotary piston engine. Because Since the cycle takes place in one half of the quadratic plane of the working chamber, for clarity, the other half can not be considered because of the repeatability of all processes that will be rotated 180 ° relative to the cavity under consideration.

The following window numbering processes are visible in this animation:

1-6 - the process of suction of the air-fuel mixture;

6-9 - the compression process of the air-fuel mixture;

9-11 - the process of pushing into the combustion chamber;

11-16 - combustion process and stroke;

16-21 - the process of pushing the exhaust gas.

In this animation, one full cycle is 2.5 turns of the main shaft and corresponds to 900 ° of the angular movement of the crank. In this case, the angular displacement of the rotor vertices per cycle relative to the coordinate axis of the center of the chamber will be 300 °. Given the duration of the full cycle and alternating them after 0.5 turns, we can draw a conclusion about the operating mode of this engine, which determines the number of simultaneously participating cycles:

m = n _shaft : Δn _cer = 2.5: 0.5 = 5,

where n _shaft is the number of revolutions per cycle;

Δn _cher - step of alternating cycles.

This proves that this engine will operate in a 5-cylinder piston engine mode.

From the ratios of the rotation of the rotor and the shaft, you can determine their gear ratio

n _mouth = n ' _mouth + n _r = 1/3 + 1 = 4/3;

N = n _r : n _mouth = 3/4,

where n _mouth is the rotation of the rotor relative to the neck of the crank;

n ' _mouth - the rotation of the rotor in the coordinate system, equal to 1/3 n _about ;

n _r is the revolution of the main shaft;

N - gear ratio relative to the working chamber or the fixed coordinate system XOY.

Figure 4 shows the design of RPD with opposite processes of cycles in two projections, where the internal arrangement of elements and parts is shown on the upper projection with a frontal section along the axis of the shaft, and in the lower projection with the removal of the upper end cover of the motor housing.

The toroidal rotor pos. 1, made of ChKh32 material, with openings made therein for passing the flow of cooling air between the combined casting elements, consists of a rim, radial-rod ribs and a central sleeve of the outer sleeve of the sliding bearing. At the same time, it is mounted on the crank neck of the main shaft, item 2, consisting of two elements of the St15X material, where their connection at the border of the crank neck in the upper earring will be provided with a fastening and threaded connection from St5. A closed partition of the working chamber pos. 3, consisting of material ЧХ32, crimped along the end surfaces in bores with end caps pos. 6 and 7 of the engine housing using gasket-fireproof material pos. 41, made of non-ferrous metal.

End caps are basically based on internal elements with adjacent surfaces composed of material ЧХ32. In the hollow designs of the covers, cooling of the heated sides adjacent to the working chamber is provided, as well as for collecting in one and distributing the flow of coolant in the other cavity of the water cooling jacket. The flow of coolant, closed through the discharge and supply pipelines pos.25 and 26 of the material AKCh, provides heat removal to the external environment. In the central part of each end cover, there is one through bushing of the outer race of the plain bearing pos.40 and adjacent through channels adjacent to them around the circumference of pos.4 to ensure the cooling air flow of the internal cavities of the rotor, the working chamber and the shaft. The cooling of the water-cooling jacket, pos. 39, is provided by a closed partition pos. 8 made of AKC material, crimped along the end surfaces by the end caps of the case, and also by disk partitions pos. 37 on the outer surface, covering the end caps of the same material, crimped by the fastener 30. from St40X. An additional housing, item 9 from St30, is attached to the outer surface of the lower end cover to separate the exhaust air-oil flow from the inner cavity of the chamber and the clutch system device. In the lower central part, the additional housing has a sleeve hole for the sliding bearing of the driven shaft, as well as a shirt fastener for separating the air-oil flow pos.21 from St30 and separating and removing heated cooling air through the collector cavity pos.38. Oil condensed in the bottom of the cavity, pos.24, is discharged through the pipe pos.23 to its cooling system. From the assembly manifold, the cleaned air is sent through the pipe pos.22 to the engine carburetor for disposal. In this case, fresh air flows through the holes in the protective casing pos. 14 and then through the air filter pos. 11 enters the cooling system. The movement of the cooling air flow will be ensured by rotation of the main shaft and the created vacuum on the back side of the fixed leading thrust heel pos. 15 with blade finning like a centrifugal wheel, with the function of an air supercharger. The transmission of rotation under load will be provided in the axial direction through the friction disk pos.16 mounted on the leading heel. The driven thrust heel pos. 17, interlocked with the lever-rotary device pos. 20, has longitudinal movement along the splines of the driven shaft pos. 19 from St15X and the spring pressing it pos. 18 from steel 60С2.

Opposite gas distribution for simultaneously occurring 5 cycle processes is provided by lever-rotary devices pos.13 from St15X, when exposed to a three-jaw disc pos.12 from St15X, which is mounted on the opposite end of the main shaft between the air filter and the upper end cover of the housing. In this case, the operation of each valve for all cycles will be determined by their location on the partition of the working chamber: for suction pos.31, for compression and discharge pos.32, for the stroke of pos.33 and for exhaust gas pos.34.

Remote tubular combustion chambers, item 27, consisting of VTZ-1 or N70MF material, will form spaces for burning air-fuel mixtures. The beginning of the combustion processes of air-fuel mixtures will be carried out with electric discharges on spark plugs pos. 28, installed by threaded connections in the nests of the combustion chambers.

Electricity for own needs will be provided by the generator pos.10, which is located on the protective casing in the inner space of the air filter.

It is proposed to start the RPD with a starting engine installed in compliance with the tightness of the connection on the adjacent housing pos. 42 from St30 to the additional engine housing. The rotation transmission from it to the leading thrust heel will be provided through the intermediate gear pos. 43 from St40X. The shaft pos.44, rigidly connected to the intermediate gear, is used to transmit rotation to the oil pump pos.45 of the lubrication system of sliding bearings and the rotor sealing system in the working chamber.

Figure 5 shows the appearance of the power unit in two projections, where 1 is the main engine housing, 2 is an additional housing, 3 is the gearbox, 4 is the main gearbox, 5 is the carburetor, 6 is the starter, 7 is the air supply manifold -fuel mixture, 8 - exhaust manifold.

Claims (1)

A four-stroke rotary piston engine, consisting of a housing, a single-stage crankshaft and a rotor crank freely rotating on the neck of the crank in the cavity of the quadratic chamber, characterized in that the motor housing is made in the form of two elements of closed partitions of the quadratic type, one inside the other, and also closing their two end caps, which compress these partitions, while the cavity formed by a small closed partition serves as a working chamber, and the cavity between the partitions serves as a water jacket hlazhdeniya, the compressed combustion air-fuel mixture is carried out in the overflow tubular combustion chambers, located in the jacket water cooling and injection pockets closing valves and stroke.

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