RU2009341C1 - Birotatory engine - Google Patents

Abstract

FIELD: engine engineering. SUBSTANCE: engine has rotor made of a drum with inner triangle working surface and two-tops piston which is positioned within it and provided with an inner rectangular groove conjugated with a rectangular output shaft. Top side of the drum is provided with ribs and passages for flowing cooling air. A system for cooling the piston is rigid. The combustion chambers are provided within the piston and made of a cylindrical groove with an axis parallel to the axis of the engine. The chambers can be in communication periodically with a nozzle made in face wall of the case. EFFECT: enhanced efficiency. 13 dwg

Description

 The invention relates to the production of internal combustion engines, in particular to rotary engines.

 In rotary engines, there is no main disadvantage of piston engines, i.e., a crank mechanism that converts the reciprocating motion of the piston into rotation of the power take-off shaft. Rotary engines are small in size and weight, better balanced.

 For example, the DKM-54 biotic engine (the “Wankel engine”) is known, made according to the epitrochoid scheme with an internal envelope and the ratio of the radii of the pitch circles of the movable and stationary gears as two to three (see. Rotor piston engines, V. S. Beniovich and other, - M., "Engineering", 1968, p. 11-13).

 The engine housing consists of two lateral parts and a middle rotating part with an epitrochoid cavity, inside which a rotor-piston of a triangular shape rotates. A rotating housing that performs the cylinder function of a classic reciprocating internal combustion engine and a rotor-piston are interconnected by a system of gears and rotate in the same direction around stationary axes passing through their centers of gravity. Power is taken from the intermediate shaft of the gear system.

 The volumes of the working chambers formed by the lateral and rotating (middle) parts of the housing and the rotor-piston are sequentially changed, which provides the conditions for the processes of intake, compression and ignition of the hot mixture, expansion and release of working gases. To seal the radial gaps between the tops of the rotor-piston and the epitrochoid surface of the middle body, sealing elements (radial plates) are installed at the tops of the rotor-piston.

 The disadvantages of the engine are the supply of high voltage to the rotating spark plugs, the difficulties of supplying a combustible mixture and the removal of combustion products from rotating parts, the presence of a gear system to synchronize the rotation of the rotors.

 The closest technical solution, selected as a prototype, is a bi-rotational engine, made according to the hypotrochoid scheme with an internal envelope and the ratio of the radii of the pitch circles of the movable and fixed gears as three to two (see, “Rotary-piston engines”, V. S. Beniovich and dr., M. "Mechanical Engineering", 1968, p. 8).

 The design of the engine can be similar to the DKM-54 engine with the only difference being that the profile of the hypotrochoid working cavity of the rotating part of the body has the form of an equilateral triangle with convex sides and rounded vertices, and the profile of the rotor-piston has an elongated oval shape.

 The engine is dynamically well balanced, has the largest dimensions and weight.

 However, the combustion chamber (the smallest volume of the working chamber formed by the side and rotating parts of the housing and the rotor-piston) has a very elongated shape and unfavorable conditions for the combustion of the combustible mixture are created in it, the smallest possible (attainable) volume of it has a certain finite value and depends only on the parameters the engine itself. The compression ratio of the combustible mixture is small, which causes certain difficulties in creating the most economical diesel option and does not allow to increase the efficiency of the engine. The alternating change in the angle of inclination of the end surface of the radial plates to the hyprochoid surface of the housing leads to a significant abrasion and deterioration of the seal due to the formation of a wedge-shaped gap between the surfaces of the plate and the housing, as a result of which gas leakages from the cavity where combustion occurs are relatively greater than in a conventional piston engine. In addition, the violation of compaction in any cavity can cause a breakthrough of hot gases and ignition of a fresh charge in an adjacent cavity (working chamber). The presence of a gear system for synchronizing rotor rotation reduces the mechanical efficiency of the entire engine structure.

 The aim of the invention is to increase engine efficiency by eliminating the special (additional) synchronizing rotation of the working bodies (rotor-piston, rotating part of the housing) mechanical connection, increasing the compression ratio of the combustible mixture, improving the combustion conditions of the combustible mixture and more reliable sealing of the working cavities (working chambers ), as well as an increase in engine life due to a decrease in the degree of wear of radial sealing elements (radial plates) mounted on the tops of the piston rotor.

This goal is achieved by the fact that the rotational engine contains:
- a supporting body, which consists of two parts forming an internal cavity in which an external rotor (hereinafter referred to as a drum) that performs a cylinder function of the engine freely rotates between the working walls on the support rollers and the working piston function of the engine rotates inside the drum in the same direction the rotor (rotor-piston-slider, hereinafter - the piston), while two working chambers of variable volume are formed between the working surfaces of the drum and piston and the side walls of the housing, in which cabins thermodynamic processes of the internal combustion engine: an inlet and air compression, formation and ignition of the combustible mixture, expansion (power stroke) and release of the working gases. On the working walls of the housing there are windows for purging and charging the working chambers with atmospheric air;
- a drum, which is a straight cylinder with an internal through working space (working cavity), the cross section of which has the form of an equilateral triangle with convex sides and rounded vertices. Three working surfaces (sides) of this space are formed by parts of a cylindrical surface of a certain radius, and the conjugation of working surfaces (fillet) is formed by parts of a cylindrical surface of a smaller radius, while the angular magnitude of the arc of each element is 60 ^about . The mates are, as it were, depressions with respect to the axis of the drum;
- a piston having a symmetrical elongated oval shape in cross section (two segments folded along chords with rounded apices). The two working surfaces of the piston are formed by portions of the cylindrical surface a radius, and coupling working surfaces (rounding) - parts of cylindrical surface of smaller radius, the magnitude of the angular elements arc of greater radius is equal to ⁶⁰ and smaller radius - ^120. Mates are like vertices with respect to the axis of rotation of the piston. Each piston working surface is provided with at least one combustion chamber, for example, of a cylindrical shape, and the combustion chamber itself communicates with the external adjacent space of the working surface. The piston together with the drive shaft form the lowest planar kinematic pair, for which the rotary cavity has an internal through cavity with plane-parallel working surfaces, and the drive shaft is equipped with a rectangular link rigidly connected to it. The reciprocating movements of the rotor occur along its longitudinal axis and perpendicular to the axis of the drive shaft, and the torque (rotation) to the drive shaft is transmitted using the guide link.

 According to the invention, the working surfaces of the drum and piston are formed by parts of cylindrical surfaces of larger and smaller radii, which are respectively equal for the drum and for the piston, which together ensures during the operation of the engine a tight and full fit (of any) one working surface of the drum and one the working surface of the piston when they come together at the end of the compression process. In this case, the working fluid (air for the variant with internal mixture formation or combustible mixture for the variant with external mixture formation), enclosed in the space between the indicated surfaces of the drum and piston and the working walls of the housing, completely flows into the corresponding combustion chamber, which can have any arbitrary wide limits volume and shape parameters, which ensures a higher compression ratio and better combustion conditions of the combustible mixture and, as a result, an increase in engine efficiency.

In the process, the interaction of the main moving parts of the engine occurs according to the following law. The piston, simultaneously rotating around its own axis and translationally moving along the guide link, in a section of a circular path, the angular value of the arc of which is 120 ^° , and the center of the arc lies in a plane passing through the rotation axis of the drum and the drive shaft, its vertices alternately engaged with the hollows of the drum. And if one vertex is engaged, then the other slides along the opposing cavity of the engagement of the concave surface of the drum. When the piston makes a half turn, its tops will change the nature of their movement to the opposite, taking a new position in the drum. Thus, in one full revolution of the piston, each radial plate at its vertices will encircle only one third of the working surface of the drum. In addition, during the operation of the engine, the angle of inclination of the end surface of the radial plates to the parts of the surfaces of unequal curvature, generally forming the working surface of the drum, is zero (the exception is the intermediate sections adjacent to the interface line of surfaces of different curvatures and equal to the thickness of the radial plate, during the transition period, the edge of the radial plate is located, which is located on the side of the working chamber with the highest pressure of the working fluid at that moment. are reliable sealing of the engine working cavities and minimum wear of the radial plates.

Comparative analysis with the prototype shows that the inventive bi-rotational engine is characterized in that:
- profiles of the forming surfaces of the drum and piston are outlined by arcs of circles of identical radii;
- obtaining any necessary degree of compression of the working fluid is ensured by a constructive choice of the volume of the combustion chamber, the full flow of the working fluid from the working chamber to the combustion chamber, respectively, and a more efficient radial sealing of the working chambers;
- more efficient (complete) combustion of the combustible mixture is ensured by a constructive choice of the shape of the combustion chamber;
- during the operation of the engine, the angle of inclination of the end surface of the radial plates to the parts of the surfaces of unequal curvature, generally forming the working surface of the drum, is zero;
- there is no additional (special) mechanical connection of the drum and piston, synchronizing their rotation.

 Thus, the inventive biotic engine meets the criteria of the invention of "novelty."

 Comparison of the claimed solution not only with the prototype, but also with other technical solutions in this technical field did not allow us to identify in them the features that distinguish the claimed solution from the prototype, which gives the right to conclude that the criterion of "significant differences".

The drawing shows a bi-rotational engine, where:
- in FIG. 1 shows a General view of the engine with local cuts of the left cover, the left side of the housing, the working wall of the left side of the housing and the drum;
- in FIG. 2, 3, 6, and 8 show, respectively, engine sections along the planes A-A, BB, G-D, D-D;
- in FIG. 4 separately shows a piston with a drive shaft;
- in FIG. 5 shows a section through a piston along a plane EE;
- in FIG. 7 schematically shows one of the possible options for the relative positioning of the drum, piston, fuel input channel and the purge windows of the engine with an eccentric drive shaft;
- in FIG. 9-12 schematically shows the relative position of the drum, piston, fuel inlet channel and engine blowdown windows, the piston and the drive shaft with a guide link of which form the lowest plane kinematic pair, respectively, at the initial moment of rotation of the drive shaft (fig. 9 conditionally) and then through each the eighth of the turnover (after 45 ^o );
- in FIG. 13 schematically shows the nature of the contact of the radial seal of the piston with the working surface of the drum.

 The bi-rotational engine consists of a drum 1, a piston 2, a drive shaft 3 (Figs. 1 and 3), a left 4 and a right 5 side covers and two parts of the casing - left 6 and right 7 (Fig. 2 and 3).

 Both parts of the housing are centered using the support ring 8 and pins 9, rigidly connected by bolts 10 (Fig. 1 and 3) and equipped with exhaust windows 11 for the exit of cooling air (Fig. 1 and 2). On the working wall of the left side of the housing 6 there are a purge window 12 (Figs. 1, 3, and 6) and passage windows 13 (Fig. 2). Similarly, on the working wall of the right side part 7 of the housing there are a purge window 14 (Fig. 3) and passage windows 15 (Fig. 8). For the passage of cutting fluid, each part of the housing is provided with a groove 16. The grooves respectively have a message with channels 17 and 18 (Fig. 3 and 8) and windows 19 and 20 (Fig. 8 and 9) having a sector profile of a circular ring. On the left side of the housing there is a threaded hole into which the fitting 21 is screwed (Fig. 3 and 6) for connecting the engine to the air compressor. On the right side of the housing 7 there is an exhaust window 22 (Fig. 3) for exhausting exhaust gases and a nozzle 23 is installed (Fig. 2 and 3).

 The drum 1 is supported by rollers 24 (FIGS. 1 and 3) located between the support ring 8 and the groove of the middle part of the outer cylindrical surface of the drum. On the side surfaces of the drum in the grooves are installed sealing elements 25 (Fig. 1 and 3), and on the cylindrical part on the sides there are compressor vanes 26 (Fig. 1, 2, 3 and 8).

 The piston 2 is located inside the drum and mounted on the drive shaft 3. On the side surfaces of the piston in the grooves are installed sealing elements 27 and 28 (Figs. 1 and 4), and on the tops of the piston there are radial plates 29 and 30 (Figs. 4, 5, 10 and 13). The piston is equipped with combustion chambers 31 (Figs. 2, 4, 5, and 11). Inside the piston there is a cavity with two plane-parallel working surfaces, which in turn is divided into two cavities 32 and 33 (Figs. 4, 5 and 9) by the drive shaft.

 The working surfaces of the drum and piston are formed by parts of the cylindrical surfaces of larger and smaller radii, which are equal for the drum and for the piston, respectively.

 The drive shaft 3 is provided with a guide link 34 (Figs. 3, 4 and 11) of a rectangular profile that is rigidly connected with it (made as a whole). The drive shaft is supported by rolling bearings 35 (Fig. 3) installed in the right and left parts of the housing.

 The side covers 4 and 5 were fastened with screws 36 (Figs. 1 and 3). Both covers are provided with inlet windows (FIGS. 1 and 2) for the passage of cooling air.

 The rotational engine operates as follows.

The piston, interacting with its movement with the drum and through the guide link with the drive shaft, rotates them around its own axes. The drive shaft, piston and drum rotate in the same direction (arrow C in Fig. 9-12). In FIG. 9-12 schematically shows the relative position of some elements of the main engine assemblies every 45 ^{about the} rotation of the piston during a half-turn.

At the same time, the piston tip 38 in the section of the circular path I-K (Fig. 9), the angular value of the arc of which is 120 ^° , and the center of the arc lies in the plane passing through the axis of rotation of the drum and the drive shaft, is in constant engagement with the working cavity 40 the cavity of the drum. Another piston peak 39 (right in FIG. 9), ahead of the rotation of the drum, slides along its concave working surface 43 (FIG. 10). And so on, until the right piston vertex 39 occupies the initial position of the left vertex 38, and the left - the right one (the drive shaft will make half a revolution around its axis during this time). Further, the piston peak 39 is in constant engagement with the cavity 42 of the working cavity of the drum in the portion of the IK path, and the piston peak 38 slides along the concave working surface 45 of the drum. Then the piston tip 38 is in constant engagement with the cavity 41 of the drum working cavity in the IK path section, and the piston peak 39 slides along the concave working surface of the drum 44, etc. In this case, in the drum working cavity bounded on the sides by the left working walls and the right parts of the engine housing, on both sides of the piston two working chambers 46 and 47 (Fig. 10 and 11) of variable volume are formed.

At the largest value of the volume of the working chamber, the purge windows 12 and 14 are maximally open (Fig. 12) - the process of purging and charging the working chamber with atmospheric air coming from the compressor occurs. With the beginning of the movement of the piston inside the drum (rotate: the drive shaft and the drum around its axes, the piston simultaneously around its axis of the drive shaft due to the possibility of translational movement of the piston along the guide link of the drive shaft), the volume of the working chamber decreases. Further, the purge windows are blocked by a drum (Fig. 10), after which the process of compression and flow of a fresh charge of air into the combustion chamber begins (Fig. 10-12). At the end of the compression process using the nozzle 23, fuel is injected into the combustion chamber 31 through the channel 48 (Figs. 2, 10 and 12) - a combustible mixture is formed, which, due to the high temperature of the compressed air, spontaneously ignites and burns. With the release of heat during fuel combustion, the temperature and pressure of the resulting working gases in the combustion chamber increase. Under the influence of working gas pressure, the piston moves in the drum and interacting with the drum through its hollows and with the drive shaft through the guide link of the drum and the drive shaft around their own axes. In this case, the working gases flowing from the combustion chamber into a volume-increasing working chamber expand and complete the work. At the end of the expansion process, purge windows open and the process of purging the working chamber begins. The same processes occur in another working chamber (on the other side of the piston), but they are phase shifted by 180 ^° . So if there is a purge in one chamber - into another fuel injection, the formation of a combustible mixture and its self-ignition and, if there is an expansion process in one chamber - into another compression process.

 Thus, in one complete revolution of the piston, two cycles of the processes of a conventional two-stroke internal combustion engine with internal mixture formation occur in the engine.

 The purging and charging of the working chambers is carried out by the air coming from the compressor through the fitting 21 into the cavity 49 (Figs. 3 and 6), formed by the left cover 4 and the left part 6 of the engine casing. Further, air through the purge window 12 enters the working chamber, displacing exhaust gases from it, which through the purge window 14, the cavity 50 (Fig. 3), formed by the right cover 5 and the right part 7 of the engine housing, and the exhaust window 22 exit.

 The working walls of the engine housing and the drum are cooled by atmospheric air, which is sucked in through the inlet windows 37 of the covers in the cavity 51 (Figs. 2, 3, and 6), then through the passage openings 13 it enters the compressor blades 26 of the drum and is discarded through the outlet windows 11 of the housing out.

 The piston is cooled using a cutting fluid as follows. Two piston cavities 32 and 33, limited laterally by the working walls of the engine housing, due to the nature of the piston movement, change their volumes from a certain minimum to a certain maximum and vice versa (Fig. 9-12). At the time when the volume of any cavity increases, it communicates with the window 20 on the left side 6 of the engine housing and through the groove 16, channel 17 and pipe 52 (Fig. 3) due to the resulting vacuum is filled with a cooled cutting fluid entering from the dispenser capacity of the heat exchanger. When the volume of the cavity decreases, the cutting fluid through the window 19 in the right part of the housing 7, the groove 16, the channel 18 and the pipe 53 (Fig. 8) are displaced into the receiving and filling tank of the heat exchanger.

 Radial plates 29 and 30 with both edges of their end surface 54 (Fig. 13) at all phases of the piston movement simultaneously touch the working surface of the drum. An exception is the intermediate sections adjacent to the line 55 (Fig. 13) of the interfaces of surfaces of different curvature and equal to the thickness of the radial plate, while the edge of the radial plate that closes the working chamber with the highest working pressure at that moment works (touches) during the transition period body.

 The above design of the bi-rotational engine relates to two-stroke internal combustion engines with internal mixture formation of the combustible mixture.

 If the purging and charging of the working chambers is carried out not with air, but with a combustible mixture and forcibly ignited at the end of compression, then we will have a two-stroke biotative engine with external mixture formation and forced ignition of the combustible mixture. The operation of this engine is as follows.

 When the purge windows are fully open (the corresponding chamber has the largest volume), the working chamber is purged and charged with a combustible mixture. As soon as the drum blocks the purge windows, the compression process begins. At the end of the compression process, the combustible mixture is forcibly ignited and the expansion process begins (working stroke). At the end of the expansion process, purge windows open and the process of purging and charging the working chamber with a fresh charge of the combustible mixture begins. In the future, all processes are repeated.

 If instead of a drive shaft 3 with a guide link 34 and a piston 2 in the described engines, use the power take-off shaft 56 with an eccentric 57 and a piston 58 with a central bore, respectively (Fig. 7), then we will get two more versions of biotic engines in which the piston is in process engine runs freely rotates on the cam shaft of the power take-off around its own axis and at the same time around the axis of the power take-off shaft. To cool the piston, it has an internal cavity, and the power take-off shaft is hollow with a central partition and radial holes near it. Cutting fluid is forcibly injected from one of the shaft ends and through its radial hole (to the baffle plate) enters the piston cavity, washes it and is discharged from the other shaft end through the shaft radial bore (after the baffle plate). The remaining interactions of the moving parts of the engines are similar to those described above.

 The increase in engine life is due to the low wear of the radial sealing elements of the working rotor due to more favorable conditions for their contact with the working surface of the drum, as well as due to their lesser cyclic run (slip) along the working surface of the drum.

 The increase in engine efficiency is due to an increase in the compression ratio and the improvement of the combustion conditions of the combustible mixture due to the possibility of constructive selection of more favorable parameters of the volume and shape of the combustion chamber, as well as more reliable sealing of the working cavities (chambers) of the engine.

 A comparative analysis shows that with equal values of the main parameters (power, fuel consumption, liter power, efficiency), the proposed engine will have smaller dimensions and weight. (56) UK patent N 957531, cl. F 1 F, publ. 1964.

Claims (1)

 BIROTATIVE ENGINE with internal mixture formation and self-ignition of the combustible mixture from compression, comprising a composite housing with a cylindrical edge and a working cavity, in which a composite rotor is installed, including a drum with a figured cavity mounted on rolling bearings, and a piston in it mounted on the output shaft, gas distribution bodies made in the end surfaces of the body cavity in the form of channels and windows, on the one side - discharge, and on the other - exhaust, means of fuel supply - in the form of nozzles, syst cooling the drum, piston and the housing and the combustion chamber, characterized in that, in order to increase efficiency in operation and simplify the design, the shaped cavity in the drum in cross section is made triangular with sides outlined by conjugate arcs of circles of equal radii, the piston - two-vertex, conjugate with cavity arcs and a rectangular through groove located symmetrically to a plane passing through the tops of the piston, the output shaft is of rectangular cross section with two planes conjugated with large planes the piston groove, the gas distribution windows are located in the drum at a radial distance greater than the smallest radius of the drum cavity, but smaller than the largest radius to its top, the drum cooling system is made with channels and ribs located on its outer cylindrical surface symmetrically with respect to the drum bearing and made in the form of centrifugal fans, with the possibility of communication with channels in the housing, located radially to the axis of rotation of the output shaft, and in the most remote place on one the purge air inlet channel and to the other exhaust gas outlet channel, the piston cooling system is made liquid, the fluid inlet port from the housing to the piston is located on one end wall of the housing cavity first from the top dead center in the direction of rotation of the rotor and symmetrically to it with respect to a straight line, which is the line of intersection of the planes of symmetry of the drum, perpendicular to the axis of its rotation, and the body passing through the axis of rotation of the shaft and drum, and in outlet - the second along the piston on the opposite wall, and the axes of both windows are located in a plane perpendicular to the specified axis of symmetry and passing through the axis of the output shaft, while the windows are made in the form of ring sectors with an external radius smaller than the smallest radial distance to the piston surface from the axis of rotation of the output shaft at its extreme position in the piston groove, and with the possibility of communication with variable volumes of the piston cavities formed by it and the output shaft, the combustion chambers are made in the piston in in the form of a cylindrical groove with an axis parallel to its axis, and with the possibility of periodic communication with the nozzle located in the housing.

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