WO2017074218A1

WO2017074218A1 - Internal combustion engine

Info

Publication number: WO2017074218A1
Application number: PCT/RU2016/000618
Authority: WO
Inventors: Сергей Вячеславович УСТИНОВИЧ; Леонид Сергеевич УСТИНОВИЧ
Original assignee: Сергей Вячеславович УСТИНОВИЧ
Priority date: 2015-10-30
Filing date: 2016-09-09
Publication date: 2017-05-04
Also published as: RU2634457C2; RU2015146717A

Abstract

The invention is directed toward enhancing the operating efficiency and reliability of an internal combustion engine, while also simplifying the design thereof and increasing its suitability to mass production. This technical result is achieved in that an internal combustion engine is provided with a rotor section, the mechanism of which does not contain a shaft eccentric but consists of an output pin coupling and is disposed inside a triangular rotor. The output shaft of the rotor section is configured with an integral flat, triangular disk at its middle, wherein pins are rigidly fastened on both faces of said disk on the axis of each of the three vertices thereof, each pin being mounted in a bearing assembly on one of the two faces of a corresponding free eccentric in the form of a flat disk. In another similar bearing assembly on the other face of each eccentric, there is mounted a pin which corresponds to one of two removable triangle-shaped outer disks of the rotor, said pins being rigidly fastened on one each of the axes of symmetry of the three vertices of the corresponding disk. The distance between the axes of the bearing assemblies of each eccentric is equal to the length of a straight line of eccentricity on which, when the rotor section is viewed in profile, the axis of the rotor is offset from the main axis of the shaft.

Description

Internal combustion engine

The invention relates to the field of engineering, to internal combustion engines of volume displacement.

Known four-stroke rotary piston internal combustion engine (ICE) [1] Wankel volume displacement (RPD), consisting of at least one rotor section with an eccentric shaft. It is more effective than the section of the well-known and most common reciprocating internal combustion engine, also containing an eccentric shaft, in the number of strokes of the stroke in one revolution of the shaft. For each revolution of his shaft, he makes one stroke of the stroke, instead of one stroke of the stroke for two turns of the shaft in the piston section. Compared to the piston sections, the mechanism of the RPD section is simpler in design, due to the absence of a connecting rod and piston in it. It is lighter than the piston section in weight and smaller in size. However, with the same volume of the working cavity of the section, the same temperature of heating the charge of the working fluid and the degree of compression, the Wankel RPD section is capable of generating a smaller moment of force on its output shaft than the piston section. As you know, it is this particular physical parameter that is transmitted to the input shaft of the load mechanism from the output shaft of the heat engine. The reason for the small value of the moment of force is the smaller geometric length of the lever arm of the shaft of the mechanism of the Wankel RPD section of the same working volume as the piston section. As you know, the value of the length of the shoulder of the shaft lever in sections with an eccentric shaft is within the eccentric length e of the eccentric, rigidly fixed to this shaft. With the same working volume of the sections, the eccentricity value of the e section of the RPD is less than 2.8 times in the piston section.

This lag in the length of the shoulder of the shaft lever does not even correct the fact that the stroke of the working stroke, that is, the duration of the selection of mechanical energy from a heated charge the working fluid in the stroke of the stroke, in the rotor section is 1.5 times longer - 270 degrees of the angle of rotation of the eccentricity against 180 degrees at the piston section. In this case, the mechanism of the RPD section in the operating mode of the stroke of the working stroke functions as a multiplier, in which for one revolution of the input power link - the rotor, its output power link - the eccentric shaft makes three full turns. This reduces the amount of mechanical energy transferred to each degree of the angle of rotation of the load shaft, reducing the efficiency of the engine.

The closest in technical essence and the achieved result to the proposed solution is a four-stroke rotary internal combustion engine [2], in the section of which the above-mentioned disadvantages inherent in the Wankel RPD section are eliminated.

It is known that the number of strokes of the working stroke in the section of any eccentric mechanism is determined by the number of revolutions of its eccentricity e, and the working stroke in the heat engine section with such a mechanism begins only when the eccentricity e is located in the so-called top dead center. At this moment, for example, the rotor face of the rotor section is in the position of the minimum compression volume of the stator epicycloid (epitrochoid) sector, where the spark plugs are installed. Since the section of the rotary engine [2] does not have a rigid attachment of the eccentric to the output shaft of the section, then for each one revolution of the shaft, the number of revolutions of the eccentrics free from rigid coupling with the shaft is greater than in mechanisms with an eccentric rigidly fixed to the shaft . In this section, synchronously rotating eccentrics make three of their full revolutions for every one revolution of the shaft. A power clutch is used there as a power unit, in which, as in any mechanical clutch, the number of revolutions of any of its two power links is always the same. These power links of the pin coupling are the rotor and shaft. Depending on the direction of transmission of mechanical energy, one power link is the leading one and the other is the driven one. In the operating mode of the stroke of the working stroke, the rotor is the leading (input) link, and the shaft is the driven (output) link. Thus, in one revolution of the rotor, the mechanical energy of each stroke of the working stroke is transmitted through the coupling one revolution of the shaft three times. Therefore, the section of this engine works as a thermal gear motor, in this case as an internal combustion engine, given that heat is supplied to the charge of the working fluid inside the working cavity of the section of this engine at the beginning of the stroke of the working stroke. That is, for each revolution of its rotor and shaft in the ICE-gear section, the cycle energy is three times more often the working stroke is selected from the heated working fluid. In total, for one revolution of the shaft from the rotor, three times more energy is transferred to it than in the Wankel RPD section and six times more than in the piston engine section of the same displacement. And compared with these sections, the efficiency of the ICE section is significantly higher.

In the RPD section and the piston section, the generator of the final product of the activity of the heat engine — the torque produced by its shaft — is the shaft eccentric. Thus, in the kinematic diagram of the mechanism of a classical engine there is an energetically ballast link - a transmitter of charge forces to the moment generating unit, that is, to the shaft eccentric. The function of the transmitter of the charge forces in the RPD is performed by the rotor, and in the piston section a piston group. As a result, the entire magnitude of the force of the heated charge in the stroke of the working stroke in transit passes through the rotor or piston, which forces them to increase reliability, increasing the weight, dimensions of the structure and, accordingly, the cost. At the same time, the increased inertial mass of parts negatively affects the amount of mechanical energy loss inside the mechanism, that is, its efficiency.

Due to the rigid fastening of the eccentric on the shaft in the mechanisms of the Wankel RPD section and in the piston section, the lever of the force moment generator - the shaft eccentric, continuously has a point of support on the root axis of the shaft, limiting the length of the arm of the lever of the moment of force to the length of its eccentricity e.

In the ICE-gearbox section [2], the moment of force generator is directly the input power link of the mechanism — the rotor, because there is no force transmitter in it. The lever of rotation of the generator of the rotor moment at each current point in time is a straight line of the perpendicular drawn from the point where the pitch circles of the program gears of the stator and rotor touch each other, into which the straight line of the eccentricity e is geometrically continued from the rotor axis beyond the main shaft axis. this limit the length of the arm of the lever of the moment increases three times to three lengths of eccentricity - Ze due to the ratio of the radii of the pitch circles of the program gears of the stator and rotor 2e: Ze, which The second one, in fact, determines the number of revolutions of the free eccentrics of the section [2], equal to three for one revolution of the rotor and shaft. A three-fold increase in the lever leads to a three-fold increase in the value of the rotor torque of the ICE-gear section compared to the Wankel RPD section of the same working volume. Which also leads to increased efficiency of the rotary internal combustion engine. Since in the section profile due to the eccentricity of the movement of the rotor axis with respect to the shaft axis, the moment of rotor force cannot be transferred to the load mechanism shaft, it must be transformed at the moment of the output shaft force of the mechanism of the same section of the ICE gearbox. That is, the input shaft of the load mechanism is able to take on a moment of force for its rotation only from a similar in design and coaxial output shaft of the heat engine mechanism. The transformation of the rotor moment of force at the moment of the shaft force of the ICE-gearbox section occurs through the mechanism of the power pin drive clutch, in which the rotor and shaft are its only two power links. As you know, any mechanical coupling practically without changes translates the value of the moment of force from one of its power link to another.

As a result of the transmission of the value of the moment of force without changing its value through the power links of the pin coupling, as well as as a result of eliminating the rigid attachment of the eccentric to the shaft in the ICE section, in the value of the moment of force created in its mechanism, along with the forces created in the nodes of the mechanism, other components of the moment of force — the shoulders of the levers in the links of the mechanism, whose value in the ICE-gearbox section has values higher than in the RPD section of the same working volume — have a greater influence. As you know, the value of the leverage lengths in the links of the structure is determined by the geometric features of its kinematic scheme. When an unchanged value of the moment of force in the stroke of the working stroke from the rotor to the shaft is transmitted to the ICE section of the engine, due to its larger length of the shoulder of the shaft lever, the value of the total load on the power bearings decreases compared to the shorter length of the average stroke per stroke of the shoulder of the lever of the rotor eccentrics, compared with the initial load of a heated charge on the rotor. In addition, due to the use of three eccentrics at once in the clutch, the power load for each eccentric bearing also decreased several times. Which led to a decrease in the weight and dimensions of its power bearings, and also increased the limit of their speed.

However, due to an increase in the number of power bearings, as a reason for increasing the number of risk factors for failure in work and opportunities to reduce overall work efficiency, the degree of requirement for the reliability of their work has increased in the pin coupling of the mechanism of the ICE section. The requirements expressed in the ability of the power bearings installed in the free eccentrics of the pin drive clutch to keep the set eccentricity length e in a stable framework, while unconditionally observing the unshakable basic functional the criterion for the operation of bearings is their own high work efficiency, expressed as the lowest possible value of the coefficient of friction. For example, in the piston section and in the Wankel RPD section, such conditions are fulfilled by only one power shaft eccentric bearing, over which the research work has been continuing to increase the functional efficiency for a rather long period of time.

In this regard, the presence of a section of sliding bearings in the power transmission sleeve of the mechanism of the mechanism, which have a high coefficient of friction, reduces the efficiency of the mechanism.

Also, plain bearings require for their work the cost of an increased amount of high-quality lubricating oil and its sufficiently effective cooling. This leads to complication of the engine design for the continuous supply of oil and energy to them for the operation of the oil cooler, which also increases the cost of the engine.

In addition, any sliding bearing requires a complex and sometimes unique design both for the elements of its mounting inside the rotor volume and for equipment for lubrication and oil cooling. This design is complex and time-consuming in serial production, therefore, complicates the manufacture and repair of the engine, and at the same time increases its cost.

At the same time, the presence of gaps in the sliding bearing, changing their thickness between its sliding rings, not only during operation, but also at the start and stop moments, as well as at power up and down, can lead to a noticeable change in the distance between the axes of the bearings in each of the free eccentrics the pin coupling in the section, which can provoke jamming of its mechanism. This factor reduces the degree of reliability of the engine.

Also one of the main disadvantages in the ICE-gearbox section [2] is also the presence of a detachable power shaft. Since, regardless of operating conditions, the gap between the edge of the hole in the power disk of the half shaft in which the shaft spigot connecting the half shaft is inevitably increased. As a result, the rigidity of the attachment of the half-shafts in a single shaft is lost, reducing the degree of reliability of this most loaded and important power link of the engine section mechanism. In addition, this factor serves as a serious obstacle to mass production of the engine.

Another drawback is the presence of excessive parts of the engine section mechanism, the functions of which can be transferred without damage to those parts without which the mechanism of the section can not do without. Thus, it is possible to simplify and facilitate the design.

The aim of the invention is to increase the reliability and efficiency, simplify the design and increase the degree of suitability for mass production of an internal combustion engine.

This goal is achieved by embedding the monolithic shaft and standardized rolling bearings of the power pin coupling in a new simplified configuration and composition of the components of the section mechanism of the rotary internal combustion engine, which allows localizing areas of inevitable wear of friction surfaces in the power circuit of the mechanism within one simple part, minimizing the number assembly parts of the section, unify and simplify them as much as possible, as well as increase the convenience of manufacturing, installation and dismantling the same details of construction, including in order to simplify access to those parts of the mechanism that during operation are subject to inevitable restoration or replacement during engine repair.

The invention is illustrated by drawings in figure 1 and figure 2.

Figure 1 shows the kinematic diagram of a section of an internal combustion engine. Figure 2 shows the eccentric disc of the pin coupling made in the form of a cartridge for standardized rolling bearings.

Symbols in the drawings and in the description text:

e - designation of the eccentricity of the mechanism of the section, the length of the straight line of which in the section profile of the rotor axis is separated from the root axis of the shaft;

D is the designation of the diameter of the central circle of the rotor disks and the shaft on which lie, respectively, the axis of the pinwheel of the extreme rotor disks and the pin of the shaft disk.

According to the proposed kinematic diagram of the section of the internal combustion engine (Fig. 1), inside the stator 1 containing the inner surface of the two-cavity epicycloid form, a monolithic shaft 2 is mounted with rotation in its main bearings, in the middle of which a flat disk 3 of the shaft is installed along its main axis, having a triangular profile and made integral with the shaft 2. On the axis lines of each of the three vertices of the disk 3 shaft from each of its two planes coaxially located tsevki 4 of the disk 3 of the shaft, which are made integral with the disk 3. That is, the shaft 2, its disk 3 and all the tsevka 4 are made of a single metal billet.

One free eccentric 5 is installed on each shaft 4 of the shaft disk with the possibility of rotation and its second bearing, whose axis is spaced from the support on the pin 4 by the length of the eccentricity line e, the eccentric 5 is mounted on one of the three pin 6, each which inside the rotor volume is made in one piece with one of the extreme flat disks 7, one coaxially mounted in one of the extreme sections along the root axis of the shaft on the rotor 8. That is, each extreme rotor disk 7 together and all its lugs are also made s from a single metal billet.

The profiles of the rotor 8 and its two extreme disks 7 have a triangular profile, and their axes coinciding with each other are parallel to the main axis of the shaft 2, from which they are spaced apart by the length of the eccentricity line e. Each pin 6 of the rotor disk 7 is located on the axis of one of three vertices of the triangular profile of the disk 7.

In this case, the axis lines of the yokes 4 and 6 also lie, respectively, in the disk 3 of the shaft and in each of the disk 7 of the rotor on the lines of the central circles, of the same diameter equal to the same value D. And each disk 7 of the rotor is removable, that is, with the possibility of dismantling and mounting on the rotor 8.

In the body of each disk 7 of the rotor, the internal teeth of the software (synchronizing) gear 9 of the rotor are cut, the axis of which is pine and the axis of the profile of the rotor 8. Its teeth are engaged with the external teeth of one of the program gears

10 stator, coaxial with the root axis of the shaft 2 and one rigidly fixed in one of the two stator flanges. The ratio of the radii of the pitch circles of the software gears 10 of the stator and 9 of the rotor is 2e: Ze.

Each free cam 5 is a flat disk, in each plane of which parallel to its axis one non-through circular hole is made, in each of which a standardized ball bearing 1 1 is rigidly fixed with its outer ring (Fig. 2). The rectilinear distance between the axes of the through holes in the eccentric disk 5 and, accordingly, the pair of bearings 11 is equal to the length of the eccentricity e.

During operation of the section through the rings and rolling elements of each of the bearings

11 of each eccentric 5 passes the amount of mechanical energy, under the combined effect of which, due to the simultaneous operation of all bearings 11 of all eccentrics 5, the parts of the power circuit move mechanism of the engine section in the range between the charge of the working fluid and the flywheel of the shaft. In this regard, the bearings 11 are the only power bearings through which the generated mechanical energy in the engine is transferred from the heated charge of the working fluid and, accordingly, the output shaft of the internal combustion engine mechanism to the input shaft of the load mechanism.

The only known alternative to the split shaft is only a monolithic shaft installed in at least two extreme main bearing bearings of the stator flanges. Which is used in the mechanism of the proposed internal combustion engine. Compared with the prototype, this increases the reliability of the engine.

Moreover, the monolithic shaft 2 is also one of the links in the new general set of elements representing the mechanism of the section of the proposed internal combustion engine.

To comply with the conditions of high reliability of the operation of the pin coupling, which is the mechanism of the ICE gear section itself, it is necessary to completely eliminate the possibility of creating gaps between the axes of the pair of power bearings 11 of each free eccentric 5, which can shift the distance between these axes beyond the specified length of the eccentricity e.

However, in order to technically reduce the observance of this condition only to the scale of one detail — the free eccentric 5, and to localize the development of a possible problem by the framework of the indicated pair of its bearings 11, it is necessary to ensure that such gaps are nowhere else formed on the entire path of the mechanical energy distribution of the power circuit in sections of the internal combustion engine gearbox in the range between the charge of the working fluid and the flywheel of the shaft. Therefore, in the mechanism of the proposed engine section, all tsevki 4 and all tsavki 6 are made monolithic with their bearing parts, respectively, the disk 3 of the shaft and the disk 7 of the rotor. In this case, one of the lugs 4 is pressed into the inner ring of one rolling bearing 11 from the side of one plane of the disk of one eccentric 5. One of the lugs 6 from the side of the other plane of the disk of the same eccentric 5 is pressed into the inner ring of the other bearing 11. And each of these two bearings it is also pre-pressed with its outer ring into one of the two through holes of the disk casing of this free eccentric 5, in which it is rolled for reliability. In this case, the observance of the calibrated distance with the length of the eccentricity e between the axes of the pairs of bearings 11 in the eccentric 5 and the mechanism of arrangement of all the spindles 4 and 6 on their supporting parts 3 and 7 specified in the proposed design is ensured by the accuracy of modern general-purpose processing machines, even without using specialized equipment.

In the proposed section, inside the rotor, which is the outer shell for its mechanism, instead of three power disks, as in the prototype — one rotor disk and two shaft disks — only one shaft disk 3 remained, which simplified and facilitated the construction of the section. The function of the rotor power disk was assumed by two extreme rotor disks 7. Excluding oil scraper elements and compression seal elements located on the outer surface of the rotor, the mechanism of the proposed section of the ICE gearbox consists of only seven monolithic parts. Three of them relate to the fixed stator - this is the stator housing with the inner surface of the epicycloid 1, the stator flange (not shown in the drawings) and the program gear of the stator 10. The four parts are movable - this is the rotor 6 and the removable extreme disk 7 of the rotor, monolithic shaft 2 and free eccentric 5. This is the smallest possible set of assembly monolithic parts for the rotary mechanism of a section that has significantly greater efficiency compared to, for example, the section of the well-known commercial RPM of Wankel, which also seven monolithic layout the details of its mechanism.

All the details of the proposed section of the internal combustion engine reducer are simple in design, easily interconnected into a single mechanism without observing any special conditions of relative positioning - along the root axis of the shaft, the parts are simply sequentially mounted to each other on each side of the shaft disk. This process is easily automated, which is convenient for mass production. The convenience of assembling and disassembling the mechanism is achieved, first of all, due to the fact that each of the extreme disks 7 of the rotor 8 is a separate removable part. This also makes it possible to substantially lighten the mass of the rotor 8, freeing all its internal space for the spatial evolution of the eccentrics 5, each of which in its design is a relatively small-scale part. Moreover, each disk 7 reliably supports the edges of the hollow rotor 8. Moreover, each extreme disk 7 is coaxially and rigidly mounted on the rotor 8, including using screw connections, while being on the edges of the rotor 8 are two rigid axial stops in opposite directions along its axis to ensure reliability specified by the design of the mutual fastening of the elements of the section mechanism located inside the rotor. The removable outer disk 7 also provides free and convenient access to the only structural element in the section mechanism, which in the process and as a result of engine operation inevitably wears out and needs to be restored or replaced. Such an element is each power ball bearing 11 of the eccentrics 5 of the pin coupling of the section mechanism. In the proposed technical solution, each free eccentric 5 is a cassette for a pair of power bearings 11. When assembling the engine, the inner ring of one of the bearings 11 of the cassette located on the side of the same plane of the eccentric disk 5 is first pressed onto one of the spindles 4 of the shaft disk 3, and then from the side opposite to the plane of the disk of the same cam 5 in the inner ring of its other bearing 11 is pressed one of the lugs 6 of one of the extreme disks 7 of the rotor.

Also, the cam of the eccentric 5, together with its bearings, is easily dismantled from the forearm during engine repair without the use of any unique equipment. Simplicity of design, low weight and small overall dimensions of the cartridge, as well as the possibility of using standardized ball bearings in it, determine the low cost of the cartridge, allowing you to change it together with the bearings to the same new cartridge with new bearings for each disassembly of the section. Thus, the repair time of each section is reduced, while continuously maintaining the operability of the internal combustion engine at a high level of reliability during operation, which also creates significant convenience for its serial production and repair.

Based on the proposed mechanism of the rotor section, it is possible to produce compact and high-performance rotary pumps and volume displacement compressors. List of used literature:

1. S.N. Bogdanov, M.M. Burenkov, I.E. Ivanov, Automotive Engines, Mashinostroenie Publishing House, Moscow, 1987, pp. 356–358.

2. Patent RU 2556838 C1 of 04/28/2014, F02B55 / 02, F01C1 / 22, F01C17 / 06.

Claims

Claim

An internal combustion engine consisting of at least one rotor section containing a stator with a two-cavity epicycloid profile, in the extreme flat flanges of which, with a possibility of rotation relative to its own main axis, a shaft is installed coaxially in the main bearing bearings, having a plane in a plane perpendicular to its main axis monolithic flat disk of a shaft of a triangular profile with it rigidly fixed on its plane parallel to the root axis by the spindles of the shaft disk, the axis of each of which lies at the intersection of one of the three lines of the axes of the vertices of the triangular profile of the shaft disk with a line of its central circle, and on each shaft shaft with the possibility of rotation with one of its circles, one of the eccentrics is installed, each of which is a flat disk, which with its other circle, its axis spaced from the axis the first circumference of the eccentric disk to the length of the eccentricity line, is installed in the rotor disk with the possibility of rotation relative to the axis line parallel to the main shaft axis and lying at the intersection of the line of one of the axes s of a rotor having a profile of a triangular hypocycloid, with a line of its central circle, the diameter of which is equal to the length of the diameter of the line of the central circle of the shaft disk profile on which the axis of the shaft sprocket lie, while the flat shaft disk is located inside the rotor volume and is parallel to the extreme flat rotor disks, one located in one of the extreme sections of the rotor along the root axis of the shaft, and in each of which is aligned with the axis of the rotor parallel to the root axis of the shaft, a software gear of the rotor is installed, while the rotor axis is in sludge is separated from the axis of the shaft to a length of a straight line of eccentricity, characterized in that in order to improve reliability and performance, simplify the design and improve the suitability for mass production of motor, drive shaft is located in the middle of the monolithic shaft of the section and is equipped with additional shaft handles, each extreme rotor disk is also additionally equipped with handles, rigidly fixed on its plane located inside the rotor, on the axis lines, each of which lies at the intersection of the axis line of one of the vertices of the triangular profile of the rotor disk with a line of its central circle having a diameter length equal to the diameter of the line of the central circle on which the axes of the shaft bores lie, pairwise rigidly and coaxially fixed on each of the two planes th shaft disk, while in each of the two planes of the disk of each eccentric, one non-through circular hole is made, in one of which one shaft of the outermost disk of the rotor is fixed in the bearing support, and one shaft of the shaft disk is fixed in the other hole of the bearing, moreover, each of the two extreme rotor disks is installed with the possibility of its dismantling and mounting on the rotor.