RU2351781C2 - Multi-rotor ice - Google Patents

Abstract

FIELD: engines and pumps. ^ SUBSTANCE: inventions relates to internal combustion engine and compressors. Multi-rotor ICE comprises housing, drive shaft and working rotor. The latter represents a solid body with axis of symmetry of the M-order, where M is the number of working rotor ribs sliding on over the housing cylindrical surface. The housing accommodates initiating devices and has intake and exhaust holes. The working rotor is rigidly fitted on the drive shaft. The working rotor axis of symmetry, axis of the housing circular-cylindrical surface and drive shaft axis are aligned. The housing has additional chambers representing circular cylinders intersecting the housing circular-cylindrical surface. The axes of previously mentioned additional chambers and housing surface lie in parallel. Every additional chamber houses additional rotor representing a solid body with axis of symmetry of the m-order, where m is the number of working rotor ribs sliding on over the additional chamber circular cylindrical surface. The rotor axis of symmetry makes it axis of rotation aligned with the additional chamber axis. Cylindrical surfaces of working and additional cylinders make the sliding surfaces confined by ribs. With working and every additional rotor revolving, the rib of one of them continuously slide in turn over the sliding surface of the other. ^ EFFECT: balanced structure, reduced friction forces and wear of working parts. ^ 1 cl, 4 dwg

Description

The invention relates to the field of engine manufacturing, in particular internal combustion engines and compressors.

In their technical essence, the closest to the claimed are devices (prototype) [1, 2], currently known as the Wankel rotary engine. The initiating device and gas distribution holes are located in the prototype case, and the working rotor makes a complex rotation in the inner cylindrical cavity, which is a three-dimensional figure with an axis of symmetry of order M, where M is the number of working rotor ribs sliding along the cylindrical surface of the case (for the prototype M = 3 ) Inside the rotor there is a coaxial gear located in the internal gearing with the drive shaft and transmitting the rotation of the rotor to the drive shaft. In this case, the centers of mass of the rotor and the internal gear, through which their axes of symmetry pass, move along a closed curve, which causes vibration and, as a result, relatively quick wear of parts.

Another technical solution close to the claimed device (analogue) is the well-known four-stroke rotary engine [3], in which the oval rotor, which is in internal gear engagement with the drive shaft, performs even more complex rotation. And the same drawback is inherent in this engine - the motion of the center of mass of the rotor, and the curve of motion of the center of mass has break points. The latter only exacerbates the situation.

The inventive device offers a simple technical idea, namely, that the axis of symmetry of all moving parts are their fixed axes of rotation, resulting in a complete absence of vibration. From the prototype and analog of the claimed device is a multi-rotor internal combustion engine (MRDVS) - differs in that the cylindrical surface of the housing is a round cylinder. The working rotor is rigidly fixed to the drive shaft, and the axis of symmetry of the working rotor, the axis of the cylindrical surface of the housing and the axis of the drive shaft are the same. Auxiliary cavities in the form of round cylinders intersecting the cylindrical surface of the housing are located in the housing, and the axes of the auxiliary cavities and the cylindrical surface of the housing are parallel. In each auxiliary cavity, the auxiliary rotor rotates, the axis of symmetry of which is its axis of rotation and coincides with the axis of the auxiliary cavity. The auxiliary rotor is a three-dimensional figure with an axis of symmetry of the order of m, where m is the number of edges of the auxiliary rotor sliding along the circular surface of the auxiliary cavity. The cylindrical surfaces of the working and auxiliary rotors are sliding surfaces bounded by ribs. During the rotation of the working and each auxiliary rotors, a continuous alternating glide of the ribs of one of them along the sliding surface of the other is carried out. The latter is referred to below as the principle of mutual sliding. As for the initiating device, both in the prototype and in the inventive device under this name appear either an electric candle, or a nozzle for fuel injection, or both together.

Figure 1 gives an explanation of the kinematics of the inventive device, which is implemented in two versions: a) an internal version with an internal working rotor, b) an external version with an external working rotor. The sections shown are used to calculate the basic geometric parameters and explain the principle of mutual sliding of the working and auxiliary rotors. The terms used, unless otherwise indicated, correspond to planar figures.

Internal option.

Unlike the prototype, in which the cylindrical surface of the housing along which the ribs of the working rotor slide is the so-called epitrochoid, in the inventive device, this surface is a round cylinder of radius R ₀ , the axis of the cylinder is at point O. The cross section of the working rotor is the correct one " bloated »M-gon (M is the number of edges) inscribed in a circle of radius R ₀ . A, B, ... are the vertices of the M-gon, which are the intersection points of the rectilinear edges of the working rotor with the section plane. Like the prototype, the working rotor is a three-dimensional figure with an axis of symmetry of the order of M, which, when turned through an angle of 2π / M, coincides with the original one. At point O is the axis of symmetry of the working rotor. At the same point is the axis of rotation of the drive shaft (not shown in FIG. 1), on which the working rotor is rigidly fixed. An auxiliary cavity in the form of a circular cylinder of radius r ₀ , the axis of which is located at the point O _i , is located in the housing, and the axes of the auxiliary cavity and the cylindrical surface of the housing are parallel. The auxiliary cavity intersects with the cylindrical surface of the housing. Λ and P are the intersection points of the lines (edges) of the intersection of the cylinders with the section plane. The circle of radius r ₀ contains a regular “inflated” m-gon (in this case m = 3), which is the section of the auxiliary rotor, and a, b, c are the vertices of the m-gon, which are the intersection points of the rectilinear edges of the auxiliary rotor with the section plane. The auxiliary rotor is a three-dimensional figure with an axis of symmetry of the order of m, which, when rotated through an angle of 2π / m, coincides with the original one. At the point O _i is the axis of symmetry and the axis of rotation of the auxiliary rotor. The position at which the vertices A of the working and a of the auxiliary rotors coincide at the point P is shown. Next, vertex A begins to slip along a circle of radius R ₀ , vertex a begins to slide along the line connecting the vertices A and B, vertex B continues to slip along a circle of radius R ₀ , and vertex c continues to slip along a circle of radius r ₀ . After a certain time, the vertices B and a meet at the point Λ. In this case, the curvilinear region of ABAc transforms into a curvilinear segment ac, similar to the curvilinear segment bc shown in Fig. 1, which is bounded by the arc bc of the auxiliary rotor and part of a circle of radius r ₀ . The described stage, which occurs from the side of the Λ point, can be used for the compression cycle of the gas mixture after the intake cycle or for the exhaust cycle of the exhaust mixture after the cycle stroke. The area of the curvilinear region ABAc, multiplied by the thickness of the rotor, determines the suction volume, the area of the curvilinear segment bc, multiplied by the thickness of the rotor determines the amount of compression. Their ratio determines the degree of compression. The latter depends on the values of M, m, R ₀ , r ₀ . With a constant compression ratio (i.e., for selected M, m, R ₀ / r ₀ ) and a constant rotor thickness, the suction volume varies in proportion to R ₀ ² .

The vertex a after meeting at the point Λ with the vertex B will then begin to slide around a circle of radius r ₀ . The vertex B will begin to slide along the line ab connecting the vertices a and b of the auxiliary rotor, and this slip will end when the vertices B and b coincide at point P. The process is then repeated.

From the moment of time corresponding to Fig. 1, from the side of point P, the curved segment ab transforms into a curvilinear region mirror symmetric (relative to the line passing through the O and O _i axes) shown in Fig. 1 of the ABAc region. This stage can be used for the stroke of the stroke after the compression stroke or for the intake stroke after the exhaust stroke.

The review shows that one auxiliary cavity with an auxiliary rotor rotating in it is not enough to provide a 4-stroke mode of operation of the claimed device as an engine.

We calculate the basic geometric parameters. Here:

α ₀ - angle of view of the intersection line of circles ΛР from the axis O,

β ₀ - the angle of view of the line of intersection of the circles ΛР from the axis O _i ,

Ω is the speed of rotation of the working rotor,

ω is the speed of rotation of the auxiliary rotor.

При этом схема оказалась в положении, показанном на фиг.1. После этого за время t₂ вершина В рабочего ротора переместится в точку Λ, т.е. повернется на угол

вершина a вспомогательного ротора также переместится в точку Λ, т.е. повернется на угол β₀.During time t _{1, the} vertex A of the working rotor moved from point Λ to point P, turning at an angle α ₀ , the vertex from the auxiliary rotor turned at an angle

In this case, the circuit was in the position shown in figure 1. After that, in time t _{2, the} vertex B of the working rotor moves to the point Λ, i.e. rotate a corner

the vertex a of the auxiliary rotor also moves to the point Λ, i.e. rotates through angle β ₀ .

Hence, Ωt ₁ = α ₀ ,

Excluding t ₁ and t ₂ we get

In addition, we have

The basic and obvious geometric relationship is

Substituting β ₀ , we obtain

From here we calculate α ₀ , and therefore β ₀ for the selected M, m, R ₀ and r ₀ .

We find the distance OO _i = L _in between the axes of the working and auxiliary cylinders

For angles α ₀ and β ₀ we have obvious inequalities:

It is significant that, based on equality (1), the ratio of the rotational speeds of the working and auxiliary rotors is expressed by a rational number. This means that a rigid connection between them and constant synchronization of their rotations can be achieved using gears or chain transmissions. The use of friction gears is excluded.

In Fig. 1, the lines connecting the vertices of the working rotor and the lines connecting the vertices of the auxiliary rotor have a certain shape. These lines are the guides of the cylindrical sliding surfaces (DSP) of the rotors. For the working rotor, they are determined by the functional dependence R (α), showing the distance R of the point of the line having the angular coordinate α from the axis of the rotor. The angle α, measured, for example, from the top of the rotor, varies within 2π / M≥α≥0. The function R (α) is a solution to the transcendental equation, which can be called the slip equation, which describes the sliding of the edges of the auxiliary rotor along the sliding surface of the working rotor. R (α) passes through three points called support points: two of them are adjacent vertices of the “inflated” M-gon, the third point lies on the bisector of the angle between the vertices and is located at a distance L _in -r ₀ from the axis of the rotor O. Very close to A DSP is the surface of a round cylinder whose guide in the form of an arc of a circle of radius R _C passes through the same reference points. The function R _C (α), by analogy with R (α), describes an arc of a circle. The degree of proximity between them is estimated by the parameter Δ (α) = R (α) -R _C (α). At the reference points, Δ = 0. Δ _max shows the maximum difference, as well as its sign, i.e. whichever is R (α) or R _C (α).

For the auxiliary rotor, the following functions are similarly introduced into consideration: the functions r (β), r _C (β), where 2π / m≥β≥0, δ (β) = r (β) -r _C (β) and the value δ _max . The third reference point is at a distance L _in -R ₀ from the axis of the auxiliary rotor O _i .

The values of Δ _max and δ _max depend on the selected M, m, R ₀ , r ₀ .

External option.

The description of the external variant is similar to the description of the internal variant, including expressions (1), (2), (3), (4). The quantities Δ _max and δ _max are likewise introduced into consideration.

The differences are as follows.

1. The distance between the axles

2. The third reference point for the working rotor is at a distance L _out + r ₀ from its axis O, the third reference point for the auxiliary rotor is at a distance R ₀ -L _out from its axis O _i .

The cylindrical sliding surfaces of the rotors together with the ribs form what can be called the cylindrical sliding structure (in rotary engines there are also end sliding planes of the rotors). Using this term, it can be formulated that in the claimed device, the principle of mutual sliding is fulfilled when the cylindrical sliding structures of the working and auxiliary rotors are counter-moving. Based on this, in the internal embodiment, all rotors rotate in one direction, in the external embodiment, the direction of rotation of the auxiliary rotors is opposite to the direction of rotation of the working rotor.

The review shows that the cylindrical surface of the rotors is a "swollen" side surface of the prism. When "inflating" the ribs of the prism remain on cylinders of radius R ₀ for the working rotor and radius r ₀ for the auxiliary rotor, and the lateral flat faces of the prism take a shape close to round-cylindrical. For the working rotor, in the internal version, these cylindrical surfaces remain inside the cylinder of radius R ₀ (i.e., R _C > R ₀ ), in the external version, the circular cylindrical surfaces go beyond the cylinder of radius R ₀ (i.e., R _C <R ₀ , special case for M = 2, when R _C > R ₀ ). For auxiliary rotors of both variants r _C > r ₀ .

Figures 2 and 3 show on the simplest example (M = 2, two auxiliary cavities, m = 2, with the same R ₀ and r ₀ ), how the tightness property of the cavities formed during the rotation of the rotors is realized, when moving parts are used in the construction, each of which rotates around its fixed axis of symmetry, and how the four-stroke mode of operation of the engine for the selected example is ensured.

In the cavity 1, the working stroke continues, which began after the point P passed the vertices A of the working and a upper auxiliary rotors, and at this moment or a little later, the initiating device located in the upper auxiliary cavity, called the active chamber, is triggered. The lower auxiliary cavity is called the gas distribution chamber. In the cavity 2, exhaust gas continues from the previous working stroke. When the vertices A of the working and d of the lower rotors coincide at the point ψ, the current working stroke will end and the exhaust exhaust from the previous working stroke will stop. In the cavity 3, the process of suction of the fresh gas mixture through the inlet continues, which began after point Г passed the peaks B of the working and d lower rotors. The suction process will end when the vertices B of the working and b upper rotors coincide at the point P, and the vertices A of the working and lower rotors coincide at the point G. In the cavity 4, the process of compression of the gas mixture continues, which will end when the vertices B of the working and a upper rotors arrive at the point Λ.

The working rotor both in the prototype and in the inventive device got its name due to the fact that it is he who performs the work of transferring the energy of the ignited gas mixture to the drive shaft. The gas pressure creates an angular momentum applied to the working rotor. The auxiliary rotor serves to create (of course, together with the working rotor) the necessary closed cavities inside the engine, and the angular momentum of the gas pressure forces on it in the first approximation is equal to zero until the beginning of the displacement of the spent mixture (figure 2 and 3), i.e. . until the end of the working stroke. If an engine with several drive shafts is required, the shafts of auxiliary rotors can also be used, the rotational forces to which are transmitted from the drive shaft through the main gear or chain gears.

при N<М этот угол целесообразно установить равным

где к≥1, целое.In the inventive device, the minimum number of auxiliary cavities is equal to two (one is active, the other is gas distribution). In principle, the number of auxiliary cavities can be any (as far as geometry allows). However, from the point of view of obtaining maximum power of the claimed device and achieving maximum simplicity, it is advisable to set N = M, where N is the number of auxiliary cylinders. It is obvious that N must be an even number, i.e. half of the auxiliary cylinders should be gas distribution, half - active, and they should alternate among themselves. Thus, it is advisable to choose an even number. For N = M, the central angle between the axes of two adjacent auxiliary cylinders is

when N <M, this angle should be set equal to

where k≥1, the whole.

Figure 2, 3 show that with the selected M = N = 2 for one revolution of the working rotor there are two working strokes. In the general case, the number of working strokes per revolution of the working rotor is

Shown in figure 2, 3 section of the housing of the claimed device is depicted in arbitrary form. Obviously, in the case of both options should be a cavity for cooling. The rotors must also be cooled. The greatest heat generation occurs near the chambers where the working stroke is carried out. At N≥4, heat is generated in two or more cavities, which contributes to lower temperature gradients in the housing. The working rotor can be facilitated as much as possible by removing excess metal (material) without impairing the strength characteristics and loss of tightness, and even in a lightened form it will have the properties of a flywheel. The openings for the inlet of the fresh mixture and the exhaust gas may have a slit-like shape elongated along the generatrix of the gas distribution chambers. With increasing thickness of the rotor (i.e., when it is elongated), the number of initiating devices should be increased. The inlet and exhaust openings can be located outside the auxiliary cavities, but near the intersection of the cylinders of radii R ₀ and r ₀ .

. Следовательно, рассчитанный внутренний вариант заявляемого устройства при одинаковых скоростях вращения равносилен по мощности 16-цилиндровому четырехтактному поршневому двигателю внутреннего сгорания со степенью сжатия ~6,7, с объемом одного цилиндра ~223 см³ и полным объемом 3,57 литра (для внешнего варианта соответственно 6,8, 187 см³ и 2,99 литра). В данном примере передача вращения от рабочего ротора к вспомогательным может осуществляться следующим образом: на валах всех роторов жестко закреплены шестерни, число зубьев рабочей шестерни - Z_W, вспомогательных шестерен - Z_S.Here is an example of the calculated geometric parameters of the claimed device, which is of interest, for example, for the aircraft and automotive industries. We select the diameter of the cylindrical surface of the housing 40 cm (R ₀ = 20 cm), the diameter of the auxiliary cylinders 5 cm (r ₀ = 2.5 cm), the thickness of the rotor - 10 cm, M = 4, N = 4, m = 3. Then, for the internal version, the suction volume will be ~ 223 cm ³ , the compression ratio ~ 6.7, for the external - 187 cm ³ and 6.8, respectively. The number of working strokes per revolution of the working rotor will be equal to

. Therefore, the calculated internal version of the inventive device at the same rotation speeds is equivalent in power to the 16-cylinder four-stroke piston internal combustion engine with a compression ratio of ~ 6.7, with a cylinder volume of ~ 223 cm ³ and a total volume of 3.57 liters (for the external version, respectively 6.8, 187 cm ³ and 2.99 liters). In this example, the transmission of rotation from the working rotor to the auxiliary can be carried out as follows: on the shafts of all rotors, gears are rigidly fixed, the number of teeth of the working gear is Z _W , auxiliary gears - Z _S.

We find

In the internal version, we either use a chain or install two intermediate gears. One of them is meshed with the working and any two adjacent auxiliary gears, the other connects the working and two other auxiliary gears. In the external version, you can directly hook the working gear with four auxiliary.

In the embodiment, the calculated internal Δ _max ≈65 microns, δ _max ≈-0,03 microns in external - Δ _max ≈90 microns, δ _max ≈-4 microns. Minimum clearances are achieved when processing the exact shape of the DSP.

Comparing the internal and external options, the following should be noted.

1. With the same selected parameters R ₀ , r ₀ , M, m and the same rotor thickness, almost the same compression ratios are provided, and the suction volume is slightly larger for the internal version.

2. In the external version, the coefficient of use of the cross-sectional area of the device is larger, however, it makes access to the initiating device and to the inlet and exhaust openings somewhat difficult.

3. In the external version, gears mounted on the working and auxiliary shafts can be directly engaged, i.e. you can do without the chains and intermediate gears necessary for the inner version.

4. Shown in figure 2 and 3 sketches of options drawn in accordance with the calculation of the cylindrical shape of the rotors. They indicate that at m = 2, the auxiliary rotor for the inner version has a relatively small thickness (transverse to the axis of rotation). In this case, the rotor can bend under the influence of the pressure of the ignited gas mixture. Therefore, for the internal version, m≥3 is recommended. In the external version, the thickness of the auxiliary rotor is larger and m = 2 can be chosen.

5. In the internal embodiment, a different arrangement of the inlet and exhaust openings (Fig. 4) provides the best gas-dynamic conditions for the movement of gas flows, since the angles of their rotation are the smallest. In the external version, a different arrangement of gas distribution holes does not change much.

To use the inventive device as a compressor, the active chambers are either removed or replaced by gas distribution. In principle, one gas distribution chamber is sufficient.

Due to the fact that all moving parts - rotors, gears (the chain can not be taken into account) - experience rotation around their fixed axes of symmetry, the design of the claimed device is initially absolutely balanced.

A certain difficulty in the implementation of the inventive device may be the sealing of cavities that arise during its operation. Sealing is carried out due to the sliding of the ribs of some rotors on the sliding surfaces of others or on the cylindrical surfaces of the housing and auxiliary cavities. However, if this problem is solved for the prototype, then most likely it can be solved for the claimed device. As in the Wankel engine, the rotor ribs can be made interchangeable and from the right metal. In addition, due to the immobility of the axis of rotation of the rotors, it is possible to implement the following sealing method: with high precision manufacturing of parts and ensuring the necessary thermal regime, the gaps between the sliding parts can be made identical and very small, and sealing will be carried out due to the surface tension forces of the lubricant having, as It is known for its pronounced wetting properties. Sealing with grease will also contribute to the fact that during rotation, the rotor rib drives a wave of compressed grease in front of it. With this method of sealing, the smallest friction force and the least wear on the parts will be provided.

LITERATURE

1. Hoppner E., Wankel F. BDP (German Patent) 1,088,287, kl. 46 a ⁵ 9, internat. kl. F02B. Application Date October 4, 1954

2. Froede W. BDP (German Patent) 1144052, kl. 46 a ⁵ 9, internat. kl. F02B. Application Date June 9, 1959

3. B. Schapiro, L. Levitin, N. Krak. EP 1417396, internat. kl. F01C 1/10, F01C 17/00. Publication Date May 12, 2004

Claims (1)

A multi-rotor internal combustion engine comprising a housing, a drive shaft, a working rotor, which is a three-dimensional figure with an axis of symmetry of the order of M, where M is the number of working rotor ribs that slide along the cylindrical surface of the housing, the rotation of the working rotor is transmitted to the drive shaft, initiating rotors are located in the housing devices for the working stroke and openings for the inlet of the gas mixture and exhaust exhaust, characterized in that the cylindrical surface of the housing is a round cylinder, a working rotor rigidly mounted on the drive shaft, the axis of symmetry of the working rotor, the axis of the cylindrical surface of the housing and the axis of the drive shaft coincide, in the housing there are auxiliary cavities in the form of round cylinders intersecting with the cylindrical surface of the housing, and the axes of the auxiliary cavities and the cylindrical surface of the housing are parallel, in each auxiliary cavity is an auxiliary rotor, which is a three-dimensional figure with an axis of symmetry of order m, where m is the number of edges of the auxiliary rotor, to which slide along the round-cylindrical surface of the auxiliary cavity, the axis of symmetry of the auxiliary rotor is its axis of rotation, coinciding with the axis of the auxiliary cavity, the cylindrical surfaces of the working and auxiliary rotors are sliding surfaces bounded by ribs, and when the working and each auxiliary rotors rotate, the ribs of one of them along the sliding surface of another.

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