RU2786863C1 - Internal combustion engine - Google Patents

Abstract

FIELD: rotary internal combustion engines.

SUBSTANCE: section of the rotary internal combustion engine is made with a slider-eccentric mechanism of the power coupling, in which the slider assembly consists of two identical components located inside the hollow rotor (10) mutually oppositely relative to the root axis of the shaft. Each of the two parts of the slider assembly contains a flat disk of the support guide for the slider of the outer radial edging edge of the flat disk of the inner stator epitrochoid, which in the profile is aligned with the external epitrochoid of the working cavity of the stator (1). The disk (7) of the inner epitrochoid is coaxially and rigidly fixed to the inner plane of the nearby cover (4) of the stator. The geometric semiaxis of symmetry of the profile faces of the inner epitrochoid in the profile coincide with the semiaxis of symmetry of the profile vertices of the outer epitrochoid of the working cavity of the stator (1). The outer edging edge of the inner guide epitrochoid of the stator, the forming of which is parallel to the root axis of the shaft, is supported in the profile point-wise and with the possibility of rolling by the bushings (17) of the slider's fore-ends. Each bushing (17) with the possibility of coaxial rotation is mounted on the front end (16) of the slider. Each pin (16) parallel to the root axis of the shaft is rigidly fixed on the middle pin disc (15) of the rotor radially in the middle of the arc profile of each radial face of the rotor (10) and at the intersection point of the central geometric line of a circle of arbitrary diameter with the geometric straight line of each minor semiaxis of symmetry of the profile of the hypotrochoid of the rotor (10).

EFFECT: invention enables to increase the reliability of the internal combustion engine.

1 cl, 11 dwg

Description

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

It is known that all commercially available positive displacement internal combustion engines (ICE) with a rotating power take-off shaft, which contain at least one section of the positive displacement mechanism, are built on the principle of complete absence of positive displacement surfaces in its local working cavity. friction of the links of the power chain of its mechanism, through which the transfer of mechanical energy between the gas charge of the working fluid (ZRT) and the power take-off shaft is carried out. Since, in view of the presence of a highly heated local charge gas inside the working cavity of the internal combustion engine, it is fundamentally not allowed to place power circuit friction pair units there, which, based on the principle of high efficiency and reliability of the engine, must be guaranteed continuous effective cooling and lubrication. Because it has been proven in practice that neglecting this condition inevitably leads to burnout of the lubricant, a sharp decrease in the efficiency of mechanical energy transfer, mechanical destruction of friction surfaces and emergency engine shutdown.

Since only this fundamental requirement provides the necessary high reliability and efficiency of a commercial heat engine, in commercial positive displacement internal combustion engines only sliding-eccentric mechanisms are used as a power mechanism, which, according to centuries-old practice, from the entire array of mechanisms known to date, are the only ones able to meet this stringent requirement.

Therefore, to control the process of changing the variable value of the volume V of the working cavity of the volumetric displacement of the ICE section of the volumetric displacement, the mechanical friction units of which are spatially located outside the volume of the working cavity, in each mechanism of these engines that has practical application, the so-called "slider unit" is used, which is the simplest by design, a two-link mechanical unit, both links of which are located not only outside the working cavity, but outside the power circuit of the mechanism. Since the slider assembly is never involved in the transfer of mechanical energy between the charge of the working fluid and the power take-off shaft.

One of its links is a movable, so-called "slider", rigidly fixed on the input movable power link of the section mechanism. Another link is a special, additional, supporting, guiding and fixed surface of the stator, with which the slider has a direct, continuous and current, or "creeping" mechanical contact, while making its non-stop, without slipping, cyclically repeating movements along its entire contact support fixed surfaces. The geometric shape of the outline of the fixed support surface, or the so-called "slider guide" determines, first of all, the trajectory of the slider along its two-dimensional geometric line on the plane. In the practice of heat engines, only two such geometric lines are known - this is a straight line segment and a closed circle line.

In this regard, in accordance with the geometric shape of the contact surface of the slider guide, that is, the stator contact surface supporting it, two types of design of the slider units are known: rectilinear and circular. The type of the slider assembly determines not only the trajectory of the cyclic spatial movement of the slider and the movable input power link of the mechanism on which the slider is rigidly fixed, but also the design of this power link of the volumetric displacement heat engine mechanism, which takes all the force F of the hot local volume of the gas charge of the working fluid.

The rectilinear type of the slider assembly is implemented in the so-called "piston mechanism" of the positive displacement engine [1. A.S. Arkharov, S.I. Isaev, I.A. Kozhinov and others; Under total ed. IN AND. Krutov “Heat engineering”, Textbook for students of higher educational institutions, Mashinostroenie Publishing House, Moscow, 1986, pp. 220-225, Fig. 5.1, 5.3, 5.4, 5.5], which, in turn, has two types.

The first of two types of rectilinear type of the slider assembly, which is called "crosshead", defines a continuous, cyclic, reciprocating, rectilinear and coaxial movement of a flat cylindrical piston disk inside the circular hollow working cylinder of the stator of the engine section mechanism. The locally closed volumetric displacement cavity along the cylinder axis is closed on one side by the cylinder head, on the other - by the bottom of the coaxial movable piston, which is coaxially and rigidly fixed on the cylindrical rod of the piston rod. In this case, the rod, through the thickening of its sliding friction surface, the so-called "slider", or in German "crosshead", moves along a separate, hollow, motionless and fixed on the stator cylinder coaxial with it - the so-called "crosshead guide", which is also called "Parallel", which, with its finite along its length, rectilinear form, sets a rectilinear trajectory of coaxial return movement for the slider, piston rod and piston. The gas charge of the working fluid, performing the processes of volume change in its thermodynamic cycle, shrinking and expanding, pulsates in the local space of the closed cavity of the cylindrical wall of the working cylinder along its axis between the head of the working cylinder and the piston bottom.

Through the cylindrical hinge of the crosshead, the piston rod is connected to one of the rod heads of the oscillating and at the same time linearly moving connecting rod, which through its second head at the second end of its rod in its second cylindrical hinge is connected to the circular disk of the central eccentric, eccentrically rigidly fixed to the shaft, the main axis which in the profile of the mechanism is perpendicular to the axis of the piston, piston rod and crosshead. In the profile of the mechanism, the rectilinear distance between the root axis of the shaft and the axis of the circle of the eccentric is equal to the length e of the geometric segment of the eccentricity of this slider-eccentric mechanism. Thus, the working cylinder with the piston and the pulsating volume of the working cavity are located in the radial space relative to the root axis of the eccentric power take-off shaft. The cylindrical hinge of the connecting rod head and the eccentric of the power take-off shaft - the output link of the engine mechanism, performs the function of the so-called "generator of the moment of force M", substituting for this the shoulder L of the lever e of the eccentricity of the shaft eccentric under the force F of the hot charge of the working fluid in its cycle of working stroke. In an eccentric shaft, the fulcrum of the eccentricity lever e in the profile of the mechanism is always fixed relative to the root axis of the shaft. As a result of the development of the eccentricity e by the lever under the action of the force F of the moment of force M, the shaft rotates, which is installed with the possibility of rotation about its main axis in the main bearings of the stator.

In the first, the crosshead form of the rectilinear type of the slider assembly, the slider itself and its stator support are spatially located far outside the hot working cavity of the working cylinder in the zone of comfortable conditions with the required reliability of low-temperature lubrication and cooling not only for the elements of the slider assembly, but also for both hinges friction of the power circuit of the engine section mechanism. However, it has a large overall radial dimension relative to the root axis of the shaft and along the axis of the working cylinder, as well as a large inertial mass of the moving parts of the mechanism, which is especially unfavorable in terms of inertial losses for the rectilinear type of the slider due to continuously repeating two cycles of piston acceleration to its maximum linear speed followed by two cycles of its deceleration to zero speed at the edges of the slider guide segment in each one revolution of the shaft. This design not only has low efficiency, but also increases the consumption of materials, weight and overall size of the mechanism structure, prevents an active increase in the number of shaft revolutions necessary to increase the amount of mechanical work per unit time, that is, the engine power on the output shaft.

In this regard, historically, 100 years after the appearance of a crosshead piston heat engine, the scheme of the second type of piston engine, in the section mechanism of which there is no both a rod with a crosshead and a crosshead guide located remotely from the working cylinder, has become most widespread. The function of the stator guide of the slider in the second type of the piston mechanism is performed by the working cylinder of the volumetric displacement cavity itself, and the function of the slider here is assigned to the compression rings of its gas seal located along the axis and near the bottom of the piston. At the same time, to secure the preservation of the straightness of the axial movement of the piston, a hollow piston cylinder, the so-called “skirt”, or the barrel, or in the French interpretation, the so-called “tronk”, is coaxially and rigidly attached to the piston disk from the shaft side. In this regard, the piston engine mechanism, which does not have a piston rod and a slider mounted on it, is called "trunk".

Therefore, in the second form of the mechanism diagram with a linear type of the slider assembly, the slider itself moves inside the uncomfortable zone of the volumetric displacement cavity at high temperatures of the friction surfaces and a significant lack of lubricating oil. The piston power hinge of the connecting rod is extremely close to the hot zone of the working cavity. Narrow-line compression piston rings of the hot zone of the working cylinder are an unreliable and not intended for this slider support, which counteracts the large lateral friction force of the piston, especially at the beginning of the TPX, which creates a lot of wear on the inner surface of the cylinder, significant losses of the generated mechanical energy and require even more significant quantity than in the crosshead piston mechanism, additional lubrication and cooling of the walls of the working cylinder and the piston joint.

In addition, in the mechanisms of both types of this type of slider assembly, radial charge pulsation is continuously reproduced in a locally closed space between the bottom of the movable piston and the head of the stationary working cylinder of the engine volumetric displacement cavity. And since the thermodynamic cycle of the charge of the working fluid contains a cooling process, which in the open cycle is solved by the release of the spent charge from the working cavity and the inlet of a new cold charge from the outside, then in the relatively narrow head of the working cylinder by design and energy-intensive, valve, additional, software gas distribution mechanism. In connection with all this, in the piston mechanism, one stroke of the working stroke occurs only for every two shaft revolutions in a row, which leads to the generation of a low clock frequency by the engine section ƒ = 0.5 Hz, structurally reducing the amount of fuel that can be burned in the TRX for unit of time, which prevents a quick and efficient increase in engine power, provoking a sharp increase in shaft speed, thereby underestimating the efficiency, reliability and service life of its operation.

These shortcomings of the piston engine section mechanism with a straight slider assembly are overcome in a mechanism with a circular slider assembly type. This type of slider has the so-called "rotary" engine and, in particular, the mechanism of the section of the rotary piston engine (RPD) Wankel [2. A.P. Panychev, A.P. Pupyshev, D.V. Kutuzov “Design and principle of operation of the MAZDA RX-8 rotary piston engine”, Editorial and Publishing Department of the Ural State Forestry Technical University, Yekaterinburg, 2012, p. 9 fig. 3, page 10 fig. 4, page 15 fig. 10]. It is much simpler in design and more compact in overall dimensions than a piston engine with a linear type of slider assembly, since, compared to a piston mechanism, it lacks a connecting rod, one of the power cylindrical joints and a gas distribution valve mechanism. And with the same volume V of the working cavity of the volumetric displacement, it is significantly more compact in terms of radial overall dimensions than the smallest trunk mechanism of a reciprocating heat engine in terms of these dimensions.

In the section of the rotary-piston engine, the power link of its mechanism, on which the slider is fixed, is the input link in the stroke of the working stroke, which is the prism of the rotor, which has two axial flat faces and in the profile several mutually symmetric arc radial faces with respect to its axis. All friction surfaces of not only the power circuit of the mechanism, but also the slider assembly are located inside the hollow rotor. In the geometric plane of one of the axial faces, or covers of the rotor, a flat hollow circular disk of the circular wheel of the rotor slider is coaxially and rigidly fixed. In the same geometric plane, it is in continuous rolling contact with the flat hollow circular disk of the slider stator guide wheel supporting it - the stator support wheel, which has a smaller diameter of its circumference than the rotor slider wheel. Through the circular internal cavity of the stator gear, the cylindrical rod of the engine power take-off shaft freely and coaxially passes. The movable wheel of the rotor slider continuously rolls around the wheel of the fixed slider guide of the stator support.

In order to exclude slippage of the profile of the circular wheel of the rotor relative to the profile of the circular wheel of the stator, both wheels have mutually comparable gear cutting, respectively, internal - at the rotor wheel and external - at the stator wheel. The values of the radii (diameters) and the lengths of the pitch circles of these gears have a mutually specific value, therefore they are the so-called "synchronizing gears". And this gear pair of the slider assembly itself is the synchronizing assembly of the mechanism slider. The ratio of the lengths of the radii of the pitch circles of the synchronizing gears of the rotor and stator geometrically determines the number of radial faces of the rotor. With three radial faces of the rotor, the radius of the dividing geometric circle of the movable synchronizing gear of the rotor is equal to the length 3e, and the radius of the dividing geometric circle of the synchronizing gear of the stator is equal to the length 2e, where e is the length of the straight line segment in the profile of the mechanism between the axes of the synchronizing gears of the stator and rotor. In this regard, the outer cut radial edge of the rotor profile has the form of a closed geometric curve of the hypotrochoid line, symmetrical with respect to the rotor axis, with three arc faces and vertices curved from its axis, through which the arc faces are interconnected in pairs. The hypotrochoid contains the geometric lines of its major and minor semi-axes of symmetry, in profile emanating from the axis of the rotor. On the outer peripheral axial and top surfaces of the rotor, narrow-linear gas seals of the rotor are installed in the grooves, spring-loaded in the direction of the inner surfaces of the stator.

The indicated ratio of the radii of the pitch circles of the rotor and the stator 3e: 2e determines the shape of the internal trim profile of the curve of the closed smooth curve of the geometric line of the epitrochoid of the stator working cavity, the radial profiles of the radial faces of which are mutually symmetrical about its axis. In this case, the stator synchronizing gear is coaxial with the axis of the stator epitrochoid, which is the root axis of the cylindrical hollow surface of the stator with an internal cut profile of the epitrochoid. The number of radial faces curved from the axis and vertices concave to its axis, mutually connecting the faces, is always one unit less than that of the rotor hypotrochoid, and with the so-called "trihedral" rotor, it is equal to two units. The epitrochoid also contains the geometric lines of its major and minor semi-axes of symmetry, in profile emanating from its axis. The inner hollow cylindrical surface formed by the profile of the epitrochoid, which is the working cavity of the engine section, is limited along its axis by two planes coaxial with it mutually opposite planes of the stator covers, at least on one of which the flat disk of the stator gear is coaxially and rigidly fixed.

An eccentric shaft is installed coaxially with the stator with the possibility of rotation in the main bearings of the stator caps, in the middle part of which, along the main axis and spatially inside the hollow rotor, a flat circular eccentric disk is rigidly and eccentrically fixed, the circle axis of which in the profile of the mechanism is spaced from the main axis of the stator and the shaft by distance of eccentricity e of the slider-eccentric mechanism of the motor. The power circuit of this rotary mechanism of the circular type of the slider assembly consists of only one hinge, compared with two power hinges for the piston mechanism of the rectilinear type of the slider assembly. It is a power cylindrical hinge containing two of its mutually rotating coaxial links: the central hollow circular sleeve of the rotor and the circular disk of the shaft eccentric. In the stroke of the working stroke, the force of the hot charge of the working fluid from the edge of the rotor through this hinge acts on the shoulder L of the rotating lever e of eccentricity, as well as in the piston mechanism, which has a fixed point of support in the profile relative to the root axis of the shaft, generating a moment of force M, under the action of which is the rotation of the power take-off shaft of the engine.

When the engine is running inside the working cavity of the volumetric displacement, the so-called "conveyor" movement of the charge of the working fluid inside the cavity of the volumetric displacement of the RPD section is performed above each one radial face of the rotor slider assembly rotating due to the engagement of the synchronizing gears along the planes of the covers and the curvilinear profile of the stator epitrochoids. Therefore, in comparison with the charge pulsation in the working cavity of a piston engine, the so-called "gas distribution" - the opening and closing of the gas charge inlet and outlet channels - inside its working cavity of the rotor section is produced by the hypotrochoid vertices of the planetary rotating rotor inside the curvilinear profile of the stator epitrochoid cavity, without using auxiliary ballast gas distribution devices and mechanisms.

The planetary rotation of the rotor is reproduced by the slider assembly, in which the translational movement of the point of contact, or touch along the pitch circle line of the stator gear moving along with the rotor of the pitch circle of the rotor gear, is accompanied by rotation of the rotor gear, which is produced due to its direct gear engagement with the fixed stator gear.

Also, compared to a piston engine, the Wankel rotary piston engine is more efficient, since it produces one stroke of the power stroke for each one revolution of the shaft, that is, its clock frequency is ƒ=1 Hz.

However, the Wankel RAP has the following at least five significant drawbacks. Firstly, due to objective geometric features, with the same value of the working volume V of its section, the length of the eccentricity of a piston engine is always 3 times longer than that of a rotary piston engine. Therefore, with the participation of the value of the arm length L of the rotating lever e as an equal factor, along with the value of the force F of the hot charge of the working fluid in the value of the moment of force calculated by the well-known formula M = FL and produced by the shaft of a piston engine of the same working volume, approximately the same number times is always higher than that of a rotary piston engine.

Secondly, in the stroke of the power stroke, the Wankel RPD mechanism works as a mechanical multiplier, due to which, in one complete cycle of rotation of the rotor relative to its axis, three complete cycles of rotation of the shaft relative to its main axis are performed. As a result, in order to achieve greater power by the engine, having completed a greater number of strokes per unit time, it is necessary to rotate the engine shaft and load faster than a piston engine does, in which the number of complete cycles of piston movement from top dead center (TDC) to bottom dead center point (BDC) and vice versa is always equal to the number of complete cycles of shaft revolutions relative to its own root axis. That is, in fact, the piston mechanism is functionally a mechanical clutch. At the same time, operation in the multiplier mode during the cycles of the working stroke significantly reduces the working life of the Wankel rotary piston engine.

Thirdly, the most significant drawback is the high probability of jamming in the current contact sector of the narrow profile teeth of the flat disk of the synchronizing gear of the rotor relative to the same narrow profile teeth of the flat disk of the synchronizing gear of the stator of the Wankel RPD slider assembly, due to at least a slight misalignment of one of the axes of these gears. Usually the gear of the movable rotor is subject to misalignment. What is expressed in the emergency stop of the rotor and shaft, critically reducing the reliability of the rotary piston engine.

Fourthly, the radius of the cylinder r of the RPD shaft rod cannot be greater than r = 1.5e, because the shaft passes spatially coaxially and inside the through central hole of the stator synchronizing gear, which has a radius of its pitch circle equal to 2e, and also taking into account the thickness of the circular layer of its teeth and the thickness of its radial wall. Therefore, the RPD shaft is always structurally limited in its bearing and load capacity, thereby reducing the possibility of increasing power, which reduces the efficiency of the engine.

Fifthly, at the beginning of the cycle of the working stroke of the hot charge of the working fluid, when the eccentricity lever e is in the TDC sector, the lever arm has a value close to zero: L=0. Since through the lever of the eccentricity of the eccentric shaft, the maximum at this moment in the stroke of the working stroke and the impact value of the force F of the power circuit between the hot gas charge of the working fluid and the power take-off shaft cannot reach the power take-off shaft in the form of a moment of force M, then with all its highest value the mechanical energy of the force F through the rotor, using the eccentric shaft as a pusher link, linearly presses the shaft blank through its main bearings to the stator. Therefore, at this moment, all without a trace of the energy of the maximum force F of the charge beyond the TPX slows down the shaft and is immediately utilized in the heat of heating the friction surfaces of the main bearings of the shaft, requiring them to continue the rotation of the shaft with plenty of lubrication and cooling. If rolling bearings are used for the main bearings of the shaft, then an artificial limitation of the maximum value of the force F of the charge is required, at which a certain threshold of its power on the shaft will not be crossed, so as not to mechanically destroy these bearings. Thus, the manufacturer is forced to deliberately underestimate the physical capabilities of the engine, artificially reducing the degree of efficiency of its operation. If this artificial barrier is not created, then only plain bearings can be used as main shaft bearings, which, although mechanically more reliable, are known to have low intrinsic efficiency due to large friction losses compared to rolling bearings, in which these losses are smaller. The same picture is observed in piston engines with an eccentric shaft mechanism.

The closest in technical essence and the achieved result to the proposed technical solution is the so-called clutch-rotary engine (MRD) of internal combustion [3. Patent RU 2778194 C1 dated 12/14/2021, F02B 55/02, F01C 1/22, F01C 17/00], which eliminates these shortcomings of the Wankel RPD.

In this clutch-rotary engine, a circular type of the slider assembly is also used in the rotary mechanism of the positive displacement internal combustion engine. The design of its power mechanism and its slider assembly has its own distinctive design features compared to the design features of the power mechanism and the Wankel RPD slider assembly. Namely, instead of a mechanism with a power eccentric shaft and a slider assembly on synchronizing gears in the Wankel RPD, the MRD uses, respectively, a power pinion clutch mechanism and the so-called "lantern-hypotrochoid" slider assembly of a rotary engine.

Therefore, in the design of its mechanism, there are no such structural elements of the Wankel RPD as flat circular disks of a cylindrical hinge of the power circuit: a central eccentric mounted eccentrically relative to the main axis of the shaft, and a central sleeve of the rotor, as well as circular disks of the slider assembly: stator and rotor synchronizing gears. Instead of a power eccentric shaft in the coupling-rotor motor section, a power lantern clutch was introduced into the mechanism, containing a power take-off shaft linear along its entire axial length, perpendicular to the root axis of the shaft and mutually parallel flat lantern discs of the rotor, shaft and radial eccentrics, and as well as the lantern of the rotor and shaft.

In the MRD section, the rotor is not only an input power link in the stroke of the working stroke, but, in the absence of an eccentric shaft, also a generator of the moment of force M. This is because the rotor is that solid mechanical power link of the mechanism, which, in the stroke of the working stroke, substitutes under the force F of the hot gas charge of the working fluid, which presses it on the radial face of the rotor, the shoulder L of the rotor lever with a length of 3e, in which the fulcrum moving in the direction of rotation of the rotor is located at the very current geometric support point of the circular type of the slider assembly of the geometric line of the dividing circle of the slider wheel - the former gear of the rotor, on the geometric line of the pitch circle of the guide wheel of the slider - the former gear of the stator.

Thus, in comparison with piston and rotary-piston engines, in which the function of the generator of the moment of force M is performed by the output power link of the mechanism - the eccentric power take-off shaft, in the MRD this function is performed by the input power link itself - the rotor. Therefore, mechanical pusher links that transmit force F are excluded from the power circuit, as well as the processes of transferring the force F of the charge to the TPX through the supports of the pusher links and losses in their power friction surfaces, which increases the efficiency of the rotary clutch engine. At the same time, the rotor is functionally a link-tractor, which, along the chain, pulls into rotation all subsequent links of the mechanism - radial eccentrics and a shaft. The tractor, as you know, is always more efficient than the pusher.

Due to the fact that the moment of force M is generated at the input power link when the rotor lever is supported not on the main axis of the shaft, as in mechanisms with an eccentric shaft, but on the dividing geometric circle of the former synchronizing gear of the rotor, then, firstly, the length of the rotor lever in the MWP rises to a value of 3e and therefore it is not inferior to the piston section in terms of the value of this parameter. Secondly, the lantern clutch synchronizes the number of shaft revolutions with the number of revolutions of the rotor, reducing the number of revolutions of the MRD shaft three times, in relation to the number of revolutions of the rotor in the Wankel RPD mechanism, and bringing the number of cycles of the working stroke to three in relation to one revolution of the power take-off shaft, significantly increasing the clock frequency MRD to the value ƒ=3 Hz. This significantly increases the efficiency and working life of the engine.

The moment of force M, generated by the rotor in the TRX, is transmitted by the lantern clutch to the engine power take-off shaft almost without loss due to its own higher mechanical efficiency compared to the mechanisms of the eccentric shaft. In the absence of directly mutually contacting gears of the rotor and stator in the circular type of the slider assembly, which rotated the rotor about its axis, in the kinematic scheme of the MRD, there is still a current point contact of contact between the geometric dividing circles of the rotor and the stator of the slider assembly. As in the rotor mechanism [2] of the Wankel RPD, this point contact in the rotor mechanism of the MRD still determines the current position of the rotor fulcrum on the stator. But if in the Wankel RPD the rotor had one more point of support on the stator, namely, through the power cylindrical hinge of the shaft eccentric on the root axis of the shaft, then, in the absence of this hinge in the MRD mechanism, the current indicated point of support at the point of contact of the pitch circles is the only one. And the movement of the contact point along the lines of the indicated dividing geometric circles indicates the fact of rotation of the rotor relative to its own axis during the operation of the mechanism of the clutch-rotor engine, even without using timing gears for this gearing.

Such movement and positioning of the current position of the single point of support of the rotor on the stator, specified in the circular type of the slider assembly of the rotor mechanism, is carried out by such a design of the slider assembly, which consists of circular cylindrical rods of several lanterns, which are mutually symmetrically fixed on one part of the mechanism and on which with the possibility of coaxial sliding bearing circular bushings of the slider assembly are installed. The outer cylindrical surfaces of the rolling bushings are in continuous multi-point rolling mechanical contact with their rectilinear generatrix lines with the rectilinear generatrix of the radial cutting edge of the additional flat disk, which is fixed on another part of the engine section mechanism and which in the profile is a curved closed geometric line symmetrical about its axis. In the profile of the current position of the rotor, geometric straight lines of rays drawn from the axes of the lanterns of the slider assembly and passing through the points of contact of the bushings of the lanterns with the profile of the curved line of the additional disk of the slider assembly geometrically intersect at the current point of contact of the indicated dividing geometric circles. The geometric rectilinear continuation of the current position of the central eccentricity e comes to the same point. And it is the only fulcrum of the rotor on the stator, which is also the current fulcrum for the rotor lever, which rotates the rotor when the force F of the hot charge of the working fluid is applied to it in the working stroke.

In the slider assembly of the prototype [3], instead of a pair of synchronizing gears, in the clutch-rotor motor, a lantern-hypotrochoid slider assembly is used, which consists of a slider with a profile form of an internal trihedral hypotrochoid of the rotor, the edges of which are parallel to the faces of the external trihedral hypotrochoid of the rotor. The internal hypotrochoid - the rotor slider, is installed with the possibility of rolling along the bushings of the stator support pins, which in their entirety are a multi-point slider guide. They are fixed parallel to the root axis of the stator and the shaft at the points of intersection of an arbitrary central geometric circle of the stator with geometric straight lines of minor semiaxes of symmetry of the two-cavity epitrochoid of the working cavity of the stator. This design completely lacks small narrow-profile links of mutual mechanical contact that can lead to their mutual jamming.

Round in profile, two bushings of the pins of each stator cover are located on the same diameter of the central geometric circle of the stator, arbitrary along the length of the radius. The large cross-sectional area of the hypotrochoids of the rotor slider, as well as the small diameter bushings of the stator support pins and the structurally large and limited in profile only by the line of the stator epitrochoids, the length of the diameter of the central geometric circle of the stator, on which the supporting pins of the slider guide are fixed, do not limit the diameter of the selection shaft in any way power and, accordingly, its physical carrier and bandwidth.

The slider assembly in this section of the MRD is also located outside the power chain, the links and friction surfaces of which are located between the SRT and the shaft. Therefore, the links and contact surfaces of the slider assembly between its rotor slider and the stator guide support are exposed to forces of a smaller order than in the power circuit, through which the overwhelming part of the energy of the charge operating in the TPX passes. However, at the moment of the beginning of the stroke of the working stroke, when the eccentricity e of the shaft eccentric is in the TDC sector, when the value of the lever arm e is close to zero L=0, the links and friction surfaces of the slider assembly are the first and closest to the rotor, which takes over and transmits further along circuit shock charge. At the same time, the slider assembly has the shortest chain of mechanical links necessary for proactively taking it upon itself - from the hypotrochoid slider of the rotor through the bushings directly to the stator pins - which have rigid supports on the stator covers, each of which in advance takes over and extinguishes in itself a significant proportion of the total amount of mechanical energy of the impact of a hot charge at the beginning of the TRC, converting it into the heat of heating its own links and friction surfaces, thereby unloading the main bearings.

Due to this, the degree of probability of mechanical destruction of the links and elements of the power circuit of the mechanism is reduced, increasing the reliability of the engine. Therefore, in relation to the structural elements of the shaft and the main bearings of the shaft, the lantern-hypotrochoid assembly of the MRD slider additionally acts as a so-called "damper", or a mechanical fuse, continuously ready to perform this function. In this regard, in the mechanism of the MRD section, it is possible to use more efficient rolling bearings as main shaft bearings, and there is also no need to organize measures in the MRD to artificially limit the amount of power generated by it.

However, this design of the slider assembly has a design flaw. It lies in the fact that during the operation of the engine mechanism, when passing the sector of the top of the slider of the inner hypotrochoid of the rotor of the contact sector of the outer surface of the bushing of the stator support pin, the slider with the hypotrochoid profile has the ability to temporarily stop the rolling process along the bushing, while either sliding along it, or losing contact with her. This is due to the geometric feature of the shape of the closed geometric line of the trihedral hypotrochoid of the rotor, which contains three extended sectors of its profile, having a profile with a large radius of curvature of the arcs of their radial faces, as well as mutually connecting the arcs of the radial faces of three relatively small along the length of the curvilinear profile of the sector of hypotrochoid vertices, at which the radius of curvature has a much smaller radius of curvature. Moreover, the profile of the hypotrochoid has a sharp transition from the profile of the arc of the radial face immediately to the narrow rounded profile of its top. Therefore, when approaching the bushing of the stator pin of this sector of the top of the slider, the speed of movement along the outer circumference of the bushing of the bearing pin of the contact point of the hypotrochoid rolling sharply increases. In this connection, depending on the increase in the speed of rotation of the rotor, there is a possibility of either sliding of the hypotrochoid along the surface of the sleeve, or a temporary loss of contact with the sleeve and subsequent abrupt restoration of mechanical contact when the sleeve passes to contact with the next incoming face of a large radius of curvature of the hypotrochoid.

The probability of a short-term loss of the rolling contact of the slider with its guide support can be characterized as a backlash, which in this mechanism is an abnormal and emergency event, leading to a decrease in the degree of reliability of the internal combustion engine.

The indicated drawback in the MRD section with a trihedral rotor is eliminated provided that in its slider assembly as a closed geometric surface, which in the profile without slipping rolls along the circular outer surface of the bushing of its lantern support, instead of the curve of the closed line of the hypotrochoid, with its mutually sharply different lengths radii of curvature of the profiles of radial faces and vertices, to apply another used in this mechanism - this is a closed curved epitrochoid line, in which, due to its geometric features, the radii of curvature of faces and vertices can have a mutually close value and which has a smooth mutual transition of the profiles of its curvature sectors. At the same time, in order to reliably prevent the formation of play in the slider assembly, the number of pairs of its lantern supports must be obviously more than two pairs.

The aim of the invention is to improve the reliability and efficiency of the internal combustion engine.

This goal is achieved in an internal combustion engine, consisting of at least one section of a rotary slider-eccentric mechanism containing a hollow stator, which along its geometric root axis is limited by the internal planes of two extreme, mutually opposed, flat stator covers coaxial with it, and in the radial direction it is limited by a closed inner cut edge of the inner cylindrical cavity of the stator volumetric displacement, which has a profile of a symmetrical closed curve of the epitrochoid geometric line coaxial with the root axis with geometric rays emanating from the root axis of the stator of mutually symmetrical straight lines of their small and large geometric semi-axes of symmetry, the number of which is equal to , respectively, the number of its vertices and faces, while the small semi-axes connect the rotor axis with its vertices, and the large semi-axes connect the rotor axis with the midpoints of its radial faces, also inside the stator cavity with the possibility of rotation relative to its own axis, which is parallel to the root axis of the stator and in the profile is separated from it at a distance of a rectilinear geometric segment with the length of the geometric ray of eccentricity e of the mechanism of the engine section, a rotor prism is placed flat relative to its own axis with an outer trim edge of hypotrochoid radial arc faces symmetrical in the profile, in which the number vertices and faces are one unit greater than the number of vertices and faces of the stator epitrochoid, and the profile of the hypotorochoid also contains geometric rays of mutually symmetrical straight lines of small and large semiaxes of symmetry emanating from its axis, the number of which is equal, respectively, to the number of its vertices and faces, while large the semi-axes connect the rotor axis with its tops, and the minor semi-axes connect the rotor axis with the midpoints of its radial faces, and in the inner cavity of the rotor in the middle of the height line of its prism along its axis, the rotor contains a medium flat rotor disk fixed perpendicular to it, monolithic with the rotor body, in profile containing radially and symmetrically located relative to the axis of the rotor and parallel to it of the same diameter radial relative to the axis of the rotor through circular pin holes, the number of which is equal to the number of vertices of the outer hypotrochoid of the rotor, and the geometric center of each of which lies at the point of intersection with the geometric line of the major semiaxis of each vertex of the rotor profile of the line of the geometric central circle of the middle disk of the rotor, having an arbitrary length of its radius X in its value, while in each of the indicated circular pin holes with the possibility of coaxial rotation, one flat circular disk of a radial eccentric is installed, which also contains a through circular eccentric hole , the axis of which is parallel to the axis of the outer circle of the disk of this eccentric and in the profile is located from it at a distance of a rectilinear geometric segment with the length of the geometric eccentricity e of the mechanism of the engine section, also inside the cavity stator epitrochoids with the possibility of rotation relative to the main axis of the stator in the supports of their own main bearings on the stator covers and coaxially with the main axis of the stator, a circular cylindrical shaft rod is installed, with a flat pinion disk of the shaft coaxial in its middle part and monolithic with the shaft body, as well as parallel to it, along root axis spaced from it, coaxially and rigidly fixed on the shaft by a removable shaft disk, both of which have the same profile shape of their outer cut edge, similar to the profile shape of the outer hypotrochoid of the rotor with the same number of their parallel radial faces and vertices, also the plane of the monolithic disk of the shaft is parallel to the planes of the middle disk of the rotor and the disks of the stator covers and the rotor covers, on the outer planes of which narrow-linear axial compression seals and concentric rings of the belt of oil scraper rings are installed in the grooves, spring-loaded towards the planes of the stator covers, and on the plane of the monolithic shaft disk located with sides of the removable shaft disk at the points of intersection of the geometric straight lines of the bisectors of the vertices of the profiles of the rotor disks with the geometric line of the central circle of the shaft disks, which has an arbitrary length of its radius in its value X, the same length as for the location of the through pinholes of the middle rotor disk, are located axes of the circular rods of the shaft lanterns, each of which is cantilevered and rigidly fixed on the monolithic shaft disk, and with its cantilever end rests on one of the circular holes of the removable shaft disk, each rod of the shaft lantern with the possibility of sliding rotation is coaxially installed in the eccentric hole of one of the radial eccentrics, also the slider assembly of the engine mechanism, consists of a movable rotor slider and a fixed guide for the stator support slider, with which the slider has several point supports of continuous mechanical contact in the profile and relative to which in one plane perpendicular to the root axis of the stator, it is installed with the possibility of cyclically repeating longitudinal movement without slipping, and in the inner cavity of the rotor along the root axis, the slider assembly contains circular cylindrical rods of several pincers, at the cantilever end of each of which a bearing sleeve is installed with the possibility of coaxial rotation, the outer cylindrical surface of which is in the profile is mounted with the possibility of continuous rolling relative to the trim edge of the surface of a closed symmetrical curvilinear profile of the slider assembly part, on which the slider assembly lantern bushes are continuously pointwise supported in the profile, while the lantern bushings of the slider assembly are cantilevered on the engine mechanism part inside the rotor cavity of the slider assembly lantern located in pairs on one straight geometric line parallel to the line of the main axis of the stator, and the bushings of each such pair of pins are installed mutually opposite and near each one of the two mutually opposite internal planes of the stator covers, while g the geometric axes of these lanterns in the profile are also located on the geometric line of the circle, which has an arbitrary length of its radius in terms of its value Y, and the straight line of the cut edge of the surface of the slider assembly supporting for the lantern bushings of the closed curvilinear profile of the slider assembly, which is in contact with the bushings of the lanterns of the slider assembly, is also parallel to the root axis of the stator, according to the invention, it is additionally equipped with two identical flat disks of the internal epitrochoid of the slider assembly, each of which is coaxially with the root axis of the stator cantilevered and rigidly fixed on one of the two mutually opposite internal planes of the stator covers, and in the profile the outer cut edge of each of the closed curved lines of the internal epitrochoid of the stator is located inside the cavity of the internal cutting edge of the external epitrochoid of the cavity of the volume displacement of the stator, with respect to the profile of the external epitrochoid of the working cavity, the profile of each internal epitrochoid of the slider assembly is in a position rotated relative to the stator root axis, in which the geometric lines of the minor semiaxes of symmetry of the inner epitrochoid coincide with the geometric lines of the major semiaxes of symmetry of the outer epitrochoid and at the same time the geometric lines of the major semiaxes of symmetry of the inner epitrochoid coincide with the geometric lines of the minor semiaxes of symmetry of the outer epitrochoid, also circular cylindrical rods lanterns of the slider assembly are cantilevered and rigidly fixed in the middle lantern disc of the rotor, and each of the two cantilever ends, on which the rolling sleeve is installed, of each single lantern of the slider assembly is located on the side of one of the two mutually opposite planes of the middle lantern disc of the rotor, and the axis of each of these data the lantern in the profile is located at the point of intersection of the geometric line of each minor semiaxis of symmetry of the profile of the outer hypotrochoid of the rotor with the geometric line of the central circumference of the rotor, which has an arbitrary length in its value Y and its radius a.

The essence of the invention is illustrated by the drawings in Fig. 1-11.

In FIG. 1 shows a side view, or in profile, of a section of a coupling-rotor engine with a trihedral rotor in the eccentricity position e at TDC, with the stator cover removed and the removable shaft disk removed.

In FIG. 2 shows a front view of the rotor section of a coupling-rotor engine with a trihedral rotor in the eccentricity position e at TDC, with the rotor seal elements removed.

In FIG. 3, fig. 4, fig. 5 and FIG. 6 shows the phases of the movement of the fulcrum of the lever of the trihedral rotor in the stroke of the stroke when the rotor moves after the top dead center.

In FIG. 7 shows a wheel pair of a radial eccentric.

In FIG. 8 shows a side view of the bearing disk of the radial eccentric.

In FIG. 9 shows a front view of the radial eccentric disk.

In FIG. 10 shows a side view of the radial eccentric assembly installed in the lantern through-hole of the middle rotor disk.

In FIG. 11 is a front view of the radial eccentric assembly installed in the lantern through-hole of the middle disc of the rotor.

Symbols in the drawings, in the text of the description and in the claims.

ICE - displacement internal combustion engine.

Wankel RPD - Wankel rotary piston engine.

MRD - clutch-rotary engine.

e is the geometric eccentricity of the engine mechanism.

r is the radius of the cylinder of the shaft rod, or the neck of the main bearing of the shaft.

V is the volume of the working cavity of the volumetric displacement of the internal combustion engine section.

X is the radius of the geometric circle on which the geometric axes of the lanterns of the lantern disks of the shaft and the lantern through holes of the middle lantern disk of the rotor lie in the profile of the mechanism.

Y is the radius of the geometric circle on which the geometric axes of the bushing pins of the slider assembly lie in the mechanism profile.

ZRT - gas charge of the working fluid.

TPX - stroke of the working stroke of the hot gas charge of the working fluid.

TDC is top dead center.

BDC - bottom dead center.

F is the mechanical force of the hot charge of the working fluid in the stroke of the working stroke.

L - lever arm of the moment of force M.

M - torque, or torque, or moment of force created by the force F acting on the arm L of the torque lever in the torque generator of the rotor section mechanism.

ƒ - clock frequency, measured in hertz (Hz), as the ratio of the number of cycles of the power stroke to one revolution of the engine power take-off shaft.

- обозначение сектора установки свечи зажигания.

- designation of the spark plug installation sector.

- обозначение направления вращения ротора и вала.

- designation of the direction of rotation of the rotor and shaft.

- обозначение вектора силы F.

- designation of the force vector F.

The proposed internal combustion engine consists of at least one section of a rotary slider-eccentric mechanism containing a hollow stator 1 (Fig. 1 and Fig. 2). The internal cavity of the volume displacement of the stator in the radial direction is limited by a closed trim edge of its internal cylindrical cavity of the volumetric displacement, which has a profile of a symmetrical closed geometric curve of the epitrochoid line 3 coaxial with the geometric root axis 2 of the stator, consisting of a mutually identical number and mirrored with respect to the axis 2 of the same the form of curvilinear arc lines curved from the axis of the faces, as well as mutually and smoothly connecting them vertices. In the axial direction along the line of its geometric root axis 2, the internal cavity of the stator is limited by the internal planes of two extreme mutually opposite flat covers 4 of the stator coaxial with the stator and its epitrochoid. In this case, the axial projection of the profile of the stator epitrochoid on the rotor covers has mutually perpendicular straight lines of geometric rays of their minor semiaxes 5 symmetry and major semiaxes 6 symmetry emanating from the root axis 2 of the stator, the number of which is equal, respectively, to the number of vertices and faces of the epitrochoid 3. Moreover, the vertices the lines of the epitrochoid lie on the lines of the minor semiaxes 5 of its symmetry, and the midpoints of the faces of the epitrochoid lie on the major semiaxes of symmetry 6.

On the inner plane of each one of the two stator caps, a flat disk of an additional internal two-cavity epitrochoid 7 of the stator protruding into the stator cavity is fixed rigidly and coaxially with the root axis 2. The forming straight line of the outer cutting edge of the epitrochoid 7 disk is parallel to the root axis 2 of the stator 1. Each of the two additional disks with the epitrochoid 7 profile is radially located inside the inner cutting edge of the epitrochoid 3 of the working cavity of the stator 1, therefore, in relation to it, the edge and the epitrochoid 7 itself are internal . Moreover, like the outer epitrochoid 3, the profile of epitrochoid 7 has its own mutually perpendicular geometric minor 8 and major 9 semiaxes of symmetry. A feature of spatial orientation in the profile of the mechanism is that the profile of epitrochoid 7, coaxial with the profile of epitrochoid 3, is rotated to such a position in which the minor semiaxes 8 of symmetry of epitrochoid 7 coincide with the major semiaxes 6 of symmetry of epitrochoid 3 and at the same time the major semiaxes 9 of symmetry of epitrochoid 7 coincide with small semiaxes 5 of symmetry of epitrochoid 3. That is, the profile of epitrochoid 7 relative to the profile of epitrochoid 3 is rotated by 90 degrees.

Functionally, the flat disks of the internal epitrochoids 7 refer to the slider assembly of the rotor section, and their outer shaped edges are the guides of the stator slider, on which the slider links of the engine mechanism rest, mounted on the power movable input link of this mechanism in the stroke of the working stroke - the rotor 10.

The rotor 10 is installed in the internal cavity of the stator with the possibility of rotation about its own axis 11, which is parallel to the root axis 2 of the stator and in the profile is separated from it by a straight distance with the length of the eccentricity e of the motor mechanism.

The rotor is a hollow prism, in the profile containing three radial arc faces 10, which are mutually symmetrical about the axis of the rotor and mutually geometrically interconnected in pairs through three rotor vertices. Along its axis 11, the rotor contains two flat axial faces, or covers 12 of the rotor. In the grooves on the outer plane of the covers 12, spring-loaded arc narrow-linear gas seals and coaxial rings of the belts of the rotor oil scraper seals are placed. Also, in the grooves of the tops of the rotor, its angular gas seals are placed.

The rotor profile is a closed, symmetrical about its axis 11 curved geometric line of a trihedral hypotrochoid, which has three small geometric semi-axes 13 of symmetry emanating from the rotor axis in the direction of the midpoints of the rotor faces, and three large geometric semi-axes 14 of symmetry emanating from the rotor axis in the direction vertices of the rotor profile and which are bisectors of the vertex angle profile.

Inside the rotor in the middle of the height of its prism and along its axis, as well as coaxially and rigidly with the rotor, a monolithic rotor disc 15 is fixed with the rotor, in which parallel to its axis 11 at three geometric points of intersection of three minor semi-axes 13 of symmetry with the geometric line of the central circle , that is, a pine with an axis 11 of the rotor, having an arbitrary length of its radius Y in its value, rigidly fixed along one axis of the cylindrical rods of three lanterns 16, on each of the two cantilever ends of which, on each of the flat sides of the disk 15, with the possibility of coaxial sliding rotation, one lantern bush 17. In their totality, all three lanterns 16 with six bushings 17 represent the slider of the slider assembly of the mechanism of the coupling-rotor engine section. All three bushings 17 of lanterns 16 with each of the two sides of the middle disk 15 along the rotor axis are in constant point in the profile rolling mechanical contact with the slider guide - the outer trim edge of a nearby one of the two internal flat disks of the internal epitrochoid 7, coaxially and rigidly fixed one by one on the nearby stator cover 4.

During the operation of the engine mechanism, during the rotation of the rotor, the bushings 17 without slipping and stopping roll around the guide outer smoothly variable curvature of the reference edge of the guide slider of the inner epitrochoid 7 of the stator, which is clamped by the pins of the slider moving along it without the possibility of backlash.

Rotation of the rotor in the slider-eccentric mechanism of the section of the clutch-rotary engine is carried out as a result of the conversion by the lever of the rotor of the force F of the gas charge of the working fluid expanding in the stroke of the working stroke at the moment of force M of the rotor. To transfer the moment of force M, generated by the rotor itself, to the power take-off shaft of the coupling-rotor engine, the mechanism of this section uses the so-called power pinion clutch, which includes the middle pinion disk 15 of the rotor 10 and parallel to it and located on both sides of it along main axis, two lantern discs of the shaft 18. One of them, the lantern disc 19 of the shaft, is coaxially and rigidly fixed in the middle part of the shaft inside the cavity of the rotor 10, and the other is the same in shape of its profile, removable during assembly and disassembly, the disc 20 of the shaft 18, which in the working position is also coaxially and rigidly mounted on the power take-off shaft 18 during installation. The shaft 18 is able to rotate coaxially with the main axis 2 of the stator is installed in its main bearings of the stator caps 4.

The disks 19 and 20 of the shaft 18 have the same shape of the outer cut edge of their profile, which, in terms of the number and arrangement of three radial straight edges and three rounded tops, is similar to the shape of the outer hypotrochoid of the rotor 10. In the profile, at the geometric point of intersection of each of the large geometric semi-axes of the vertices of the profile of the disk 19 of the shaft and its geometric central circle, having an arbitrary length of its radius in its value X, parallel to the root axis, a cylindrical rod of each one of the three lanterns 21 of the shaft is rigidly and cantilevered with its geometric axis. At the same time, the cantilever ends of the lanterns 21 are fixed in the through holes of the disk 20, the axes of which in the profile are located similarly to the axes of the lanterns 21 in the disk 19. Thus, eliminating the possibility of bending the lanterns 21 during engine operation.

On each one of the three lanterns 21 of the shaft with the possibility of coaxial sliding rotation with its through eccentric hole, a flat circular disk of one of the three radial eccentrics 22 is installed, which, with its outer circular surface, in turn, is installed with the possibility of coaxial sliding rotation in one of the three through circular pin holes 23 of the middle disk 15 of the rotor 10. Moreover, the geometric axes of each of the three holes 23 are located at the intersection points of the major semi-axes 14 of the hypotrochoid 10 of the rotor with the geometric central circle of the rotor profile, which has an arbitrary length of its radius in its value X, that is, exactly the same length radius X, as for fastening the pins 21 in the lantern disks 19 and 20 of the shaft 18. Three radial eccentrics 22, along with the disks 15 of the shaft and 19, 20 of the rotor, are also components of the power pinion clutch of the slider-eccentric mechanism of the coupling-rotor engine of the internal combustion.

Thrust washers 24 and 25 are coaxially and freely installed on each of the pins 21 on both sides, which, with their calibrated width, control the axial play of the rotor, relative to the disks 19 and 20 of the shaft 18, which, in turn, have axial stops relative to the stator in their main bearings .

The flat disk of the two-cavity internal epitrochoid 7 of the slider assembly, which was additionally introduced into the design of the engine mechanism, the profile of which is rotated 90 degrees relative to the profile of the external two-cavity epitrochoid 3 of the working cavity, replaced the central circular shaft eccentric, which, by its eccentric installation relative to the root axis of the shaft in the piston and rotary-piston slider-eccentric mechanisms provided a continuous position of the axis of the input in the stroke of the power link of the mechanism in relation to the root axis of the shaft in the profile at a distance of the length of the eccentricity segment e of the eccentric. As in the scheme with the so-called lantern-hypotrochoid slider assembly [3], in the proposed scheme with the so-called “lantern-epitrochoid” slider assembly, the engine mechanism also lacks the central eccentric, which is unnecessary in this mechanism, which, simultaneously with the power function, also performed the specified program function unusual for the power link.

However, in the prototype [3] and the proposed mechanisms of rotary internal combustion engines, both the lantern-hypotrochoid and lantern-epitrochoid nodes of the slider are also capable of performing a power function, but not by transferring the mechanical energy of the power circuit of the mechanism between the red-hot gas charge and power take-off shaft, and the protective function of the damper, increasing the degree of reliability of the engine design, unloading the shaft parts, and in particular the main shaft bearings, from excessive loads that occur during periods of critical loads at the beginning of the stroke cycle in the engine .

Reliable operation of the engine mechanism is also facilitated by the mutually symmetrical three-beam arrangement of the pins 16, which, with a three-beam star, cover the entire surface of the supporting guide surface of the outer edged contour of the inner epitrochoid 7 of the stator, at any time (Fig. 3 - Fig. 6) excluding the possibility of the formation of a torsional backlash in mechanical contact of the slider and slider guide, which took place in the design of the prototype [3].

The proposed lantern-epitrochoid design of the slider assembly is more compact than that of the prototype [3], since in it the entire mechanism in the profile is located inside the profile of the belt of circular coaxial oil scraper sealing rings on the covers 12 of the rotor, for which it is not necessary to change their traditional circular shape, which simplifies the design engine. Moreover, this was done while maintaining the radial standard thickness of narrow-line oil scraper rings.

Also, the radial overall dimension of the rotor section has retained its relatively small dimensions, which was also facilitated by the construction principle of the proposed slider assembly. As is known, the smaller the profile of the rotor section in terms of its cross-sectional area, the lower the material consumption of the entire structure of its mechanism and the inertial mass of the movable rotor installed relative to the eccentric axis of imbalance. As is known, the narrowing of the profile of the rotor section also leads to the need to narrow the cross-sectional area of the profile of the power take-off shaft, which leads to a decrease in the value of its bearing and throughput, reducing the efficiency of the engine. Therefore, to maintain the level of performance, the surface area of the section of the narrowest section of the shaft should not be less than at least the specific section area of the main bearing journal of the shaft required for high efficiency.

At the same time, the radial dimensions of the rotor and the proposed design of the mechanism make it possible to cut out in the central disk 15 of the rotor 10 a radially compact inner edged profile 26 of a triangular and triangular shape, coaxial with it, similar to the profile of the external triangular hypotrochoid 10 of the rotor. However, profile 26 is a three-beam star built on circular arcs, with its geometric semi-axes of symmetry and shape rotated by 60 degrees with respect to the profile and semi-axes of symmetry of the hypotrochoid 10 of the rotor. Just as the profile of the slider guide - the inner epitrochoid 7 of the stator of the lantern-epitrochoid assembly of the slider, is rotated by 90 degrees relative to the profile of the epitrochoid 3 of the working cavity of the stator. Exactly according to the same principle, a three-beam outer, radial, edged profile 27 of the middle part of the shaft is built on circular arcs, located inside the profile 26 of the central disc 15 of the rotor and located in the same secant plane with it. In this case, the profile of the three-beam star 27, by analogy with the design of the slider assembly, is also rotated by 60 degrees with respect to the three-beam profile of the disk 19 of the shaft, on which it is coaxially and rigidly fixed. At the same time, the cross-sectional area of the profile 27 of the shaft is not inferior in its value to the cross-sectional area of the neck of the main bearing of the shaft. In this design, during operation of the clutch-rotor motor, during synchronous rotation of the rotor 10 and shaft 17, the cut edges of the profile 26 of the rotor and the profile 27 of the shaft located in the same sectional plane do not come into mutual mechanical contact (Fig. 3 - Fig. 6), and while maintaining its performance, due to its design and shape of the shaft and rotor section located in the same plane, it retains the required minimum radial size of the rotor section, while maintaining a high bearing and throughput of the shaft.

The generation of the moment of force M in the stroke of the clutch-rotary engine is carried out by the power link of the engine mechanism itself, which is the rotor, which, in connection with this, is the generator of the moment of force M. For this, the rotor substitutes under the force F of the gas charge of the working fluid shoulder L of the rotor lever, the current value of the length of which is determined in the profile of the mechanism by the geometric point of application of the force vector F to it and the geometric point 28 of the lever support on the stator of the engine mechanism. As is known, the current value of the arm L of the lever is the length of the geometric perpendicular drawn from the fulcrum 28 of the lever to the line of the external force vector F applied at the point of its application to the lever. In the rotor mechanism, the point of application of the resulting force of the gas charge heated in the TPX, in view of the presence of a recess in each arc radial face 10 of the rotor, is always located in the middle of the profile of the rotor face. As a result, the direction of the force vector F always passes along the geometric line of the minor semiaxis of symmetry 13, passing into the geometric line of the major semiaxis of symmetry 14 of the rotor 10.

As is known, in the kinematic scheme of the slider-eccentric rotor mechanism, the rotor 10 has a current contact support at point 28 on the stator in the slider assembly. Namely, at the current support point of the geometric circle line coaxial along the axis 11 with the rotor 10 of the dividing circle, having the length of its radius 3e, the synchronizing gear of the rotor with the line of the geometric circle, coaxial with the root axis 2 of the stator by the dividing circle, having the length of its radius 2e, stator synchronizing gear. But regardless of the absence in the proposed mechanism of the rotary engine of flat circular disks of a classical pair of synchronizing gears, it contains all the elements of a geometric design that reproduce mutual geometric contact precisely at the point 28 of the geometric circle 29 of the rotor, coaxial with the rotor, and the geometric circle 30 of the stator, coaxial with a stator (Fig. 3 - Fig. 6). Under the action of an external force applied to the edge of the rotor in the stroke of the working stroke, or when the shaft is rotated by an external force in the expensive cycles of the four-stroke thermodynamic cycle of charge - exhaust, intake and compression, the current value of the arm L of the rotating lever 3e always rotates the power take-off shaft relative to its root axis .

In any position of the rotor, the six-link lantern support in the slider assembly of spatially spaced three bushing lanterns 16 and six bushings 17 of the rotor slider on the slider guide - the cut edge of the inner epitrochoid 7 of the stator, in the profile always geometrically ensures the convergence of the lines of three geometric rays drawn from the axis of each of their lanterns 16 and bushing 17 to the point 28 of the current touch of the geometric circle 29 of the rotor and the circle 30 of the stator under the structurally specified condition that each of the three in the data profile and spatially mutually spaced beams is always perpendicular to the surface profile of the epitrochoid 7 at the point of the current touch. And the length of the geometric perpendicular, in the profile, drawn from the fulcrum 28 of the lever to the intersection with the mutually extending geometric lines of the minor semiaxis 13 and the major semiaxis 14 of the rotor profile is at the current moment the current length of the arm L of the lever 3e of the rotor (Fig. 3 - Fig. 6) . At the same point 28 in the profile of the mechanism, a rectilinear continuation from the root axis of the shaft of the current position of the rectilinear segment of the central eccentricity e of the mechanism of the clutch-rotary internal combustion engine comes geometrically. In this case, the lines of the segments of the eccentricities e of the three radial eccentrics are always parallel to the line of the segment of the central eccentricity e located between the axes 2 of the stator and the shaft and the axis 11 of the rotor.

In FIG. 1 - fig. 6 shows the rotor section of the coupling-rotor motor, in which a flat circular disc is used as a radial eccentric 22, with the possibility of coaxial rotation, installed inside the through circular pin hole 23 of the pin middle disc 15 of the rotor 10.

But since, as is known, the rolling process of mechanically contacting friction surfaces, due to its minimal mechanical losses, is always more efficient than the sliding process, then in order to increase the efficiency of the engine, the design of the radial eccentric 22, which is shown in Fig. . 7 - fig. eleven.

In the context of the high reliability of the design of the specified critical power unit of the engine, the so-called “wheel set” of a railway car, which is known not only for its simplicity, but also for its high reliability, is taken as the basis for this type of rolling elements.

Each wheel pair of two radial eccentrics 22 mounted on a flat disk consists of one monolithic cylindrical part (Fig. 7), in which a somewhat thinned axle 31 is located along its axis in the middle part, on both edges of which the disks of two wheels 32 of a larger diameter than the diameter of the axle 31. The axial width of the axle 31 is equal to twice the width of each wheel 32. In this case, the axle 32 with the possibility of coaxial and sliding rotation is installed in the through radial hole 33 of the flat disk 22 of the radial eccentric parallel to its axis. Thus, the axle 31 of the wheelset during rotation slides along the internally cylindrical surface of the hole 33. There are two such holes on the disk 22, and their axes in the profile are located on the geometric line of the central circle, and the camber angle between them is 120 degrees. Also in the disk 22 of the radial eccentric, coaxially with each hole 33 on the side of both planes of the disk 22, non-through semicircular recesses 34 are made, each of which has a linear radial exit to the outer surface of the disk 22 for mounting coaxial placement of the wheels 32 of the wheel pair (Fig. 8, Fig. 9). Moreover, the wheels 32 do not touch the surfaces of the internal non-through holes 34 with their outer surface.

Each wheel pair is mounted on a radial eccentric from the outside in the radial direction. As an assembly, the radial eccentric 22 with wheel pairs is installed coaxially into the through pin hole 23 of the pin middle disk 15 of the rotor 10, while the outer circular surfaces of the wheels 32 of the wheel pairs are in point rolling contact with the cylindrical surface of the hole 23 (Fig. 10, Fig. 11) . Thus, each disk of the radial eccentric 22 has two internal plain bearings - with a shaft pin 21 and with an axle 31 of the wheelset, as well as one external rolling bearing, between the two wheels 32 of two wheelsets and the hole 23 of the disk 15 of the rotor 10.

The proposed rotary internal combustion engine, containing in its composition a circular lantern-epitrochoid slider assembly, can use for its operation a rotor not only with three, but also with a different integer number of its radial faces.

List of used literature:

1. A.S. Arkharov, S.I. Isaev, I.A. Kozhinov and others; Under total ed. IN AND. Krutov “Heat engineering”, Textbook for students of higher educational institutions, Mashinostroenie Publishing House, Moscow, 1986, pp. 220-225, Fig. 5.1, 5.3, 5.4, 5.5.

2. A.P. Panychev, A.P. Pupyshev, D.V. Kutuzov “Design and principle of operation of the MAZDA RX-8 rotary piston engine”, Editorial and Publishing Department of the Ural State Forestry Technical University, Yekaterinburg, 2012, p. 9 fig. 3, page 10 fig. 4, page 15 fig. 10.

3. Patent RU 2778194 C1 dated 12/14/2021, F02B 55/02, F01C 1/22, F01C 17/00.

Claims (1)

An internal combustion engine consisting of at least one section of a rotary slider-eccentric mechanism containing a hollow stator, which is limited along its geometric root axis by the internal planes of two extreme, mutually opposed, flat stator covers coaxial with it, and is limited in the radial direction a closed inner cut edge of the inner cylindrical cavity of the stator volumetric displacement, having a profile coaxial with the root axis of a symmetrical closed curve of the epitrochoid geometric line with geometric rays emanating from the stator root axis of mutually symmetrical straight lines of their small and large geometric semiaxes of symmetry, the number of which is equal, respectively, to the number its vertices and faces, while the small semi-axes connect the rotor axis with its vertices, and the large semi-axes connect the rotor axis with the midpoints of its radial faces, also inside the stator cavity with the possibility of rotation about its own axis, which is parallel to the core stator axis and in the profile is separated from it at a distance of a straight geometric segment with the length of the geometric ray of the eccentricity e of the engine section mechanism, a rotor prism is placed flat relative to its own axis with an outer trim edge of hypotrochoid radial arc faces symmetrical in the profile, in which the number of vertices and faces on one unit more than the number of vertices and faces of the stator epitrochoid, and the profile of the hypotorochoid also contains geometric rays of mutually symmetrical straight lines of small and large symmetry semiaxes emanating from its axis, the number of which is equal, respectively, to the number of its vertices and faces, while the major semiaxes connect the rotor axis with its vertices, and the minor semi-axes connect the rotor axis with the midpoints of its radial faces, and in the inner cavity of the rotor in the middle of the height line of its prism along its axis, the rotor contains a medium flat pinion disk of the rotor fixed perpendicular to it, monolithic with the rotor body, in the profile containing a radial and symmetrically located relative to the axis of the rotor and parallel to it, radial through circular holes of the same diameter with respect to the axis of the rotor, the number of which is equal to the number of vertices of the outer hypotrochoid of the rotor, and the geometric center of each of which lies at the point of intersection with the geometric line of the major semi-axis of each vertex of the profile of the line rotor of the geometric central circle of the middle disk of the rotor, having an arbitrary length of its radius X in its value, while in each indicated circular pin hole with the possibility of coaxial rotation, one flat circular disk of a radial eccentric is installed, which also contains a through circular eccentric hole, the axis of which is parallel to the axis of the outer circle of the disk of this eccentric and in the profile is located from it at a distance of a straight geometric segment with the length of the geometric eccentricity e of the mechanism of the engine section, also inside the cavity of the stator epitrochoid with the possibility axis of rotation relative to the main axis of the stator in the supports of its own main bearings on the stator covers and coaxially to the main axis of the stator, a circular cylindrical shaft rod is installed, with a flat pinion disk of the shaft coaxial in its middle part and monolithic with the shaft body, as well as parallel to it, spaced along the main axis from it, coaxially and rigidly fixed on the shaft by a removable shaft disk, and both of them have the same profile shape of their outer cut edge, similar to the profile shape of the outer hypotrochoid of the rotor with the same number of its radial faces and vertices parallel to it, also the plane of the monolithic shaft disk is parallel to the planes of the middle disk of the rotor and the disks of the stator covers and the rotor covers, on the outer planes of which narrow-line axial compression seals and concentric rings of the belt of oil scraper rings, spring-loaded towards the planes of the stator covers, are installed in the grooves, and on the plane of the monolithic shaft disk located on the side of the removable shaft disk at the points of intersection of the geometric straight lines of the bisectors of the vertices of the profiles of the rotor disks with the geometric line of the central circle of the shaft disks, which has an arbitrary length of its radius in terms of its X value, the same length as for the location of the through pinholes of the middle rotor disk, the axes of the circular rods of the pins are located shaft, each of which is cantilevered and rigidly fixed on the monolithic shaft disk, and with its cantilever end rests on one of the circular holes of the removable shaft disk, each shaft pin of the shaft with the possibility of sliding rotation is coaxially installed in the eccentric hole of one of the radial eccentrics, also the node slider of the engine mechanism, consists of a movable slider of the rotor and a fixed guide for the slider of the stator support, with which the slider has several point supports of continuous mechanical contact in the profile and relative to which in one plane perpendicular to the root axis of the stator, it is installed with the possibility cyclically repeating longitudinal movement without slipping, moreover, in the inner cavity of the rotor along the root axis, the slider assembly contains circular cylindrical rods of several pins, at the cantilever end of each of which a bearing sleeve is installed with the possibility of coaxial rotation, the outer cylindrical surface of which is installed in the profile with the possibility of continuous rolling relative to the cut edge of the surface of a closed symmetrical curvilinear profile of the slider assembly part, on which the lantern bushings of the slider assembly are continuously pointwise supported in the profile, while the lantern bushings of the slider assembly are cantilevered on the part of the engine mechanism inside the rotor cavity of the slider assembly lantern located in pairs on one straight geometric line parallel to the line of the root axis of the stator, and the bushings of each such pair of pins are installed mutually opposite and near each one of the two mutually opposed inner planes of the stator covers, while the geometric axes of these pins ok in the profile are also located on the geometric line of the circle, which has an arbitrary length of its radius in its value Y, and in contact with the bushings of the pins of the slider assembly, forming a straight line of the cut edge of the surface of the slider assembly supporting for the pintle bushings of the closed curvilinear profile of the slider assembly is also parallel to the root axis of the stator, which differs in that it is additionally equipped with two identical flat disks of the internal epitrochoid of the slider assembly, each of which is coaxially with the root axis of the stator cantilevered and rigidly fixed on one of the two mutually opposite internal planes of the stator covers, and in the profile the outer cut edge of each of the closed curved lines internal epitrochoid of the stator is located inside the cavity of the internal trim edge of the outer epitrochoid of the stator volumetric displacement cavity, while relative to the profile of the outer epitrochoid of the working cavity, the profile of each internal epitrochoid of the slider assembly is in a rotated relation relative to the root axis of the stator, the position in which the geometric lines of the minor semiaxes of symmetry of the internal epitrochoid coincide with the geometric lines of the major semiaxes of symmetry of the external epitrochoid and at the same time the geometric lines of the major semiaxes of symmetry of the internal epitrochoid coincide with the geometric lines of the minor semiaxes of symmetry of the external epitrochoid, also the circular cylindrical rods of the pins of the slider assembly cantilevered and rigidly fixed in the middle lantern disk of the rotor, and each of the two cantilever ends, on which the rolling sleeve is installed, of each single lantern of the slider assembly is located on the side of one of the two mutually opposite planes of the middle lantern disk of the rotor, and the axis of each of these lanterns in the profile is located at the point of intersection of the geometric line of each minor semiaxis of symmetry of the profile of the outer hypotrochoid of the rotor with the geometric line of the central circumference of the rotor, which has an arbitrary length of its radius in terms of its Y value.

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