RU2331770C2 - Method of power conversion in rotary screw volumetric machine - Google Patents

Abstract

FIELD: engines and pumps.

SUBSTANCE: invention relates to the method of power conversion in a rotary screw machines incorporating the first and the second set of coupled external and internal elements spaced apart along the central axis and furnished with internal/external profile surfaces. In rotary motion of internal and/or external elements, between the said elements working chambers are formed. The said working chambers move axially. The rotary motion of the aforesaid various sets is timed so that a synchronous and in-phase motions feature a different value of angular oscillation period of the working chamber axial motion. Thus, the working medium transferred by the said chambers can be either compressed or expanded. The proper timing allows optimising the machine operation.

EFFECT: optimisation of the rotary screw volumetric machine efficiency.

7 cl, 6 dwg

Description

FIELD OF TECHNOLOGY

The invention relates to a method for converting energy in a rotary screw machine.

BACKGROUND

Volumetric rotary screw machines comprise mating screw elements, namely, a female screw member and a male screw member. The female screw element has an internal profile surface (an internal screw surface covering a surface), and the male screw element has an external profile surface (an external screw surface, a male surface). Helical surfaces are not cylindrical surfaces and radially limit the elements. They are centered on axes that are parallel and which usually do not coincide and are spaced apart by a length E (eccentricity).

A three-dimensional rotary screw machine of this type is known from US Pat. No. 5,439,359, in which the male member surrounded by the stationary female member makes a planetary motion relative to the female member.

The working chambers of rotary volumetric screw machines with internal coupling are formed by kinematic mechanisms consisting of these male and female curvilinear elements.

The conversion of movements is based on the interconnected rotational movement of the male and female elements entering into mechanical curvilinear contact with each other and forming these closed working chambers for the working substance, which moves along the axis when the relative movement of the conjugated elements in space is performed.

In most cases, helical surfaces are in the form of cycloids (trochoids), as, for example, in the example known from French patent FR-A-997957 and US patent 3975120. The motion conversion used in engines is described by V. Tiraspolsky in the course “Hydraulic Well Drilling” motors in drilling "(" Hydraulical Downhole Motors in Drilling "), pp.258-259, published in the Paris edition of TECHNIP.

The effectiveness of the method of energy conversion in screw machines according to the prior art is determined by the intensity of the thermodynamic processes occurring in the machine, and is characterized by the generalized parameter "angular cycle". The cycle is equal to the angle of rotation of any rotational element (male, female, or synchronizing link) selected as an element with an independent degree of freedom.

The angular cycle is equal to the angle of rotation of the element with an independent degree of freedom, during which the entire period of change in the cross-sectional area (opening and closing) of the working chamber formed by the covered and covering elements, as well as the axial movement of the working chambers for one period P _m in machines with an internal helical surface or for one period P _f in machines with an external helical surface.

Known methods of energy conversion in volumetric rotary screw machines with conjugate elements of a curved shape, implemented in such volumetric machines, have the following disadvantages:

- limited technical potential due to an imperfect process of organizing movement, which cannot increase the number of angular cycles per revolution of the drive element with an independent degree of freedom;

- limited power density of such screw machines;

- limited effectiveness;

- the existence of reactive forces on the stationary body of the machine.

In all cases, the longitudinal axis of the screw elements of the internal interface are parallel. Sometimes they have an eccentricity and some of them can be mobile. In this case, either planetary motion or differential motion is carried out.

SUMMARY OF THE INVENTION

The aim of the present invention is to eliminate the above problems.

The volumetric screw machine used in the invention comprises at least two sets of conjugated male and female elements spaced apart, preferably along the central axis of the machine. The male elements of each set have an internal profile surface centered around the first longitudinal axis, and the male elements of each set have an external profile surface centered around the second longitudinal axis. The first and second longitudinal axes are parallel to each other. The male elements are placed in the cavity of the corresponding female elements.

In the method of converting energy in a rotary screw machine according to the invention during rotational movement of male and / or female work elements, the working cavities that are formed between female and male elements perform axial movement. According to the invention, the rotational movements of the different sets are synchronized in such a way that the synchronous and in-phase movement of the elements in the different sets is performed with different values of the angular periods of the oscillation of the axial movement of these working chambers.

In other words, parts (or elements) of the machine are arranged in such a way that, when one mating element moves, the coaxial longitudinal axes in each set move with angular velocities having values characterized by a given ratio (one in relation to the other).

Synchronization helps optimize machine performance.

In a preferred embodiment, the angular period decreases from one set to the next set, thereby compressing the working medium. In an alternative embodiment, the angular period increases from one set to another set, thus expanding the working environment.

An embodiment of the machine comprises both a rotor and a counter-rotor, the latter rotating in the opposite direction relative to the rotor. Between them can be placed planetary moving elements. This embodiment contributes to a stable and balanced movement of the working medium in the working chambers.

The clutch means may be a mechanical device. Alternatively, a working environment may be used to couple different sets. In combination of these alternatives, the synchronization means comprises (at least partially) a hollow shaft through which the working medium passes.

In another preferred embodiment, the first set is used, forming a differential kinematic mechanism having three degrees of freedom of mechanical rotation, of which two degrees of freedom are independent, and the second set, which forms a planetary kinematic mechanism, having two degrees of freedom of mechanical rotation, of which one degree of freedom independent. The third set of conjugated elements may form a differential kinematic mechanism.

The machine, in this case, can be made in such a way that the conjugate elements of the first and third sets have essentially equal sections. In other words, the first and second sets can be of the same design and can be coupled by means of the second set. In particular, the average radii and / or thicknesses and / or undulations of the screw elements are equal.

Kits, of course, may contain more elements than a single male and a single female element. In a preferred embodiment, there is a nesting structure. For example, the aforementioned first and second sets may contain two groups of conjugated male and female elements that are separated by a channel through which the working medium can be transported.

In another preferred embodiment of the method according to the invention, the thermal energy of the working medium is removed and supplied to the heat exchanger (removed from the working medium in the first stage and supplied in the second stage, or vice versa).

In addition, the mechanical energy generated in one of these kits can be used to propel another mechanical device. In other words, mechanical energy can be extracted from a rotary screw machine. Of course, the well-known laws of thermodynamics should be taken into account, in particular, at the same time, temperature changes will occur in some parts of the machine or the working medium.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention will become more clear after reading the description of the preferred variant of its implementation, which is given below with reference to the drawings, in which:

Figa is a longitudinal section of a volumetric screw machine used in the present invention;

Fig.1b is a schematic view of the volumetric screw machine of Fig.1;

Figure 2 is a section along the line II-II of Figure 1 of the volumetric screw machine shown in Figure 1;

Figure 3 is a section along the line III-III of Figure 1 of the volumetric screw machine shown in Figure 1;

4 is an illustration of how a final profile of a helical surface of any of the mating elements can be constructed; and

Figure 5 - performed in an electronic computer-aided design system, the construction of a helical surface of a conjugate element having a symmetry order n _m = 4.

DESCRIPTION OF THE PREFERRED EMBODIMENT OF THE INVENTION

The volumetric screw machine used in the present invention, which is shown in FIGS. 1a and 1b, contains three sets of conjugate elements, namely, the first set 1, which forms a differential kinematic mechanism for suction and compression of air, the second set 2, which forms a planetary a mechanism for compressing air (and for providing fuel combustion in its chamber 140), and a third set 3, forming a differential kinematic mechanism that is designed to expand the combustion products from the chambers 1 40 sets 2.

In other words, the volumetric screw machine used for the invention is a rotary screw internal combustion engine in which movement is converted, and in which a continuously cyclic change in the energy of the working substance occurs synchronously with the process of transferring this working substance through the working chambers of different compartments. Volumetric screw machine, therefore, produces the energy of the working substance. There are synchronizers 11 and 14, which are designed to support the operation of set 1 and set 3, respectively. They can be made as a single element, as shown in Fig.1b.

It should be noted that the different sets 1, 2 and 3 of the volumetric screw machine according to the invention are spaced apart from each other along the central axis Z of the machine. In other words, sets 1, 2, and 3 do not surround each other. Rather, they are placed one after the other, or, in other words, one on the line of the other. All of them are centered on the central axis of the machine.

Different sets are linked both by mechanical bonding and by the action of a gas working substance, i.e. gas connection. The mechanical connection between the mechanisms 1, 2 and 3 is provided by a conventional shaft 4, which is partially hollow, and, in addition, has a crank 10 attached to it. Air can pass from the set mechanism 1 to the set mechanism 2 through the hollow portion of the shaft 4. Sets 1 and 2 together form a rotary screw compression compression machine (compressor) of volume type. Set 2 provides combustion chambers 140, and sets 2 and 3, when working together, form an expanded rotary screw machine (expander) of volume type.

Both the first and second sets 1 and 3 contain two groups of conjugate elements, namely, the first group of elements 5, 6 and 7 (5 ', 6' and 7 ') and the second group consisting of elements 15, 16 and 17 ( 15 ', 16' and 17 ').

It should be noted that the first set 1 and the second set 3 essentially have the same shape, i.e. have the same section. This is especially true for individual screw elements: they have the same average radii and the same thicknesses.

The machine contains the following parts.

The first set contains the first female elements 5 and 15 having internal profile surfaces 105 and 115, respectively, while the female elements 5 and 15 are centered on the fixed Z axis, i.e. axis of symmetry of a volumetric screw machine. The female elements 5 and 15 have an order of symmetry 6. Further, the concept of "order of symmetry" refers to the rotational symmetry of the finite surface of these elements. The first set further comprises second elements 6 and 16, which are both male and female, i.e. contain both the outer trochoidal surface 216, 116 and the inner trochoidal surface 206, 106. They have a symmetry order of 5 and are centered on their own axis O ₆ and O ₁₆ , respectively. They perform a planetary movement. There are provided synchronizing elements 7 and 17 having an outer profile surface 207 and 217, respectively, with the order of symmetry 4. Between these elements there are working chambers 100, 300 on one side and 200 and 400 on the other side. Between the elements 5, 6 and 7 on the one hand and 15, 16 and 17 on the other hand there is a channel such that the air transported to the working chambers 100 and 200 can be returned to the lower (in FIG. 1) side of the volumetric screw machine, and then transported further to the working chambers 300 and 400.

The second set 2 contains only two conjugate elements, namely, a female element 8 having an internal profile surface 108 with an order of symmetry 3, which is also centered on the Z axis, and a male element having an external profile trochoidal surface 209 with an order of symmetry 2, which is centered on the axis O ₉ , and which performs planetary motion. Working chambers 140 are made between these elements. Fuel can be supplied through the inlet element 12 to these working chambers 140.

The third set 3 contains in each group a first male element 7 'and 17', respectively, having outer surfaces 207 'and 217', respectively, with order of symmetry 4, which are centered on the fixed axis Z. Second elements 6 'and 16', which both are male and female, contain the original trochoidal surfaces 106 ', 206' and 116 ', 216', both of which have the order of symmetry 5. These elements 6 'and 16' are centered on the second axes O _{6 '} , O _16' and perform planetary motion. Elements 5 ′ and 15 ′ having inner surfaces 105 ′ and 115 ′ with symmetry order 6 act as synchronizing elements. Between these elements, working chambers 100 ', 300' are formed on the one hand and working chambers 200 ', 400' on the other.

Set 1, shown in FIG. 1, which forms a differential mechanism, has three degrees of freedom of mechanical rotation of elements 5, 6, 7 and 15, 16, 17. Two of these degrees are independent degrees of freedom of rotation.

The same applies to elements 5 ', 6', 7 'and 15', 16 'and 17' of set 3, also forming a differential mechanism.

The planetary kinematic mechanism for converting the movement of set 2, shown in FIG. 1, has two degrees of freedom of mechanical rotation of element 9. One of its degrees is an independent degree of freedom of rotation.

According to the invention, energy conversion can be carried out by converting the movement of conjugated elements in the form of mechanically coupled movements of elements of sets of groups of the kinematic mechanism, namely, groups formed by conjugated elements 5, 6, 7, 15, 16, 17 and 8, 9, which are aligned with eccentricity in each other’s internal cavities. In addition, clutch synchronizing links 10 can be used, as well as matching devices 11 that perform synchronized, interconnected movement of elements around the main axis of the machine and around their own axes. To do this, the motion conversion is performed synchronously in at least two groups of kinematic mechanisms, where the movement of mutually conjugate elements is converted to obtain the energy of the working substance.

The method according to the invention facilitates the conversion of the movement of the conjugated elements, synchronously and simultaneously, while the working substance passes through the differential kinematic mechanisms in set 1, which are mechanically connected to each other and, for example, form a suction and compression compartment, as shown in FIG. one. At least this differential kinematic mechanism formed in set 1 has three degrees of freedom of mechanical rotation, of which two are independent, and planetary kinematic mechanisms from set 2, shown in FIG. 1, contain a compression and discharge compartment of the working substance having one an independent degree of freedom of rotation, and in the differential and planetary mechanisms there are different values of the angular periods of the axial movement of the working chambers (when counting from the angle of rotation of the output link 4).

It should be noted that screw elements cannot have an arbitrary shape and must have precisely defined properties. Their clearly defined shape d _m , which is constructed as described below, as disclosed with reference to Figure 4, where the profile d _m has a symmetry order of n _m = 5.

We start by building a hypocycloid G, which has a parametric shape (depends on parameter t):

x (t) = Ecos (n _m -1) t + E (n _m -1) cost

y (t) = Esin (n _m -1) tE (n _m -1) sint

Such hypocycloids Г with the order of symmetry n _m , (n _m +1), (n _m +2), ... (n _m + i) are those curves that are described by point A of a circle having a radius O _1A = E and center О _Е , and which was rolled (without slipping) along the inner surface of another circle with a radius equal to En _m , E (n _m + 1), E (n _m + 2), ... E (n _m + i), having center About _m , as shown in FIG. The points at which point A is in contact with these circles are denoted by B, C, D, F, I. An equivalent method of constructing such a hypocycloid с with the symmetry order n _m , (n _m +1), (n _m +2), .. . (n _m + i) is based on the description of the curve by point A of circles with radii E (n _m -1), E (n _m + 2), ... E (n _m + 1 + i) and the center O ₂ , which rolls (without slipping) along the inner surface of circles having a radius equal to En _m , E (n _m + 1), E (n _m + 2), ... E (n _m + 2 + i).

The profile D _m used for screw elements in the present invention, starting with hypocycloid G, is obtained by rolling a circle with a radius r ₀ , which is, for example, 2E, r ₀ = FR = 2E in Figure 4, along hypocycloid G, and when rolling the center of this circle moves along the hypocycloid.

If r _{0 is} selected monotonically varying along the z axis (axis perpendicular to the plane of the drawing in FIG. 1), we obtain parametric equations for the profile D _m (depending on the parameter t):

where n = n _m -1 or n = n _f -1.

Figure 5 shows a three-dimensional representation of a screw element obtained using the above construction.

All outer surfaces 217, 216, 207, 206, 217 ', 216', 207 ', 206', 209 of the male elements 17, 16, 7, 6, 17 ', 16', 7 ', 6' and 9, and all internal the surfaces 105, 106, 115, 116, 105 ', 106', 115 ', 116', 108 of the female elements 5, 6, 15, 16, 5 ', 6', 15 ', 16' and 8, respectively, are radially bounded such non-cylindrical helical surfaces constructed as described above. It should be noted that the symmetry order of these surfaces increases from the inside out. In the second set, the screw element 9 has an order of symmetry 2, while the screw element 8 has an order of symmetry 3. In the first set 1 and the third set 3, the innermost element 17, 17 'has an order of symmetry 4 and is surrounded by an element 16, 16' with an order of symmetry 5, which itself is surrounded by an element 15, 15 'having an internal profile surface 115, 115' with an order of symmetry 6. This sequence of orders of symmetry is then repeated from element 7, 7 'to element 5, 5'.

Elements 5, 7, 15, 17, 5 ', 7' 15 ', 17' are mounted so that they can rotate around the Z axis. Axes O ₆ , O ₁₆ , O _{6 '} , O _16' , O ₉ elements 6, 16, 6 ', 16' and 9, respectively, are movable. It should be noted that the O ₆ axis has an eccentricity E ₁ = E with respect to the central Z axis, and that the O ₁₆ axis has an eccentricity -E ₂ (less than E ₁ ) with respect to the central Z axis. These O ₆ and O ₁₆ axes are located on the line crossing the central axis. During rotation, their spatial relationship remains unchanged. In other words, if the eccentricities are selected so as to obtain a statically balanced volumetric screw machine, then the screw machine will also be dynamically balanced. Elements 6, 16 and 9 are installed in the machine so that they can perform planetary motion around the Z axis. Elements 6, 16, 6 ', 16' are installed between elements 5, 7; 15, 17; 5 ', 7' and 15 ', 17', respectively, without any additional means of starting the planetary motion of the rotor. The rotor 6 is pivotally mounted on the crank 10 of the shaft 4.

In the differential mechanisms 1 and 3 and the planetary mechanism 2, the connections are set up so as to make it possible to perform continuous cyclic suction with compression in set 1, compression with the release of working substance into working chambers 140 of set 2 and expansion of working substance in working chambers 100 ', 200 ', 300', 400 'of set 3. It should be noted that the combustion compartment with the combustion chamber 140 is formed by elements of the planetary mechanism 2, the cross section of which is shown in Fig.3. The planetary mechanism 2 consists of a central stationary stator 8 and a planetary satellite rotor 9, a crank 10 on the shaft 4. The device 12 is designed to inject fuel into the chamber 140 and to ensure its ignition. Combustion chambers 140 can be formed by one period of biotative movement of the profiles of elements 8 and 9 or two periods of movement (for burning fuel in a constant volume).

When the element is stationary 8, the planetary movement of the element 9 is determined by the following parameters:

ω ₈ = 0, symmetry order n ₈ = 3; n ₉ = 2; ω ₁ = ω of _{rotation (9)} = 1; ω ₉ = ω of _{rotation (9)} = -0.5. The total volume in the set 2 is set as V ₂ = (3 · V ₁₄₀ · 360/360) = 3V ₁₄₀ to rotate the shaft 4. In each set, the female screw elements 8 can be rotated about a central axis. Alternatively, element 8 may be stationary. The planetary movement of the male element 9 mating with the first element can be performed using the synchronizing coupling link-crank 10 of the third (male) mating screw element, which is coaxial with the first element.

Turning now to the first set, one can choose three kinds of state of the first group of elements 5, 6, and 7:

a) rotation (or state of immobility) of the first element 5 around the central fixed axis and rotation (or state of immobility) of the third element (synchronizer) 7 around the central fixed axis,

b) rotation of the axis O _{6 of the} second element 6 around a fixed central axis, and

c) the rotation of the second element 16 with the help of a synchronizing coupling link (covered male conjugate screw element 7), which is coaxial to the first.

These three types of states can be (mechanically) synchronized, each with the corresponding one of the second group of elements 15, 16 and 17 of the first set 1, containing:

d) rotation (or state of immobility) of the first element 15 around the central fixed axis and rotation of the third element (synchronizer) 17 around the central fixed axis,

d) the rotation of the axis O _{16 of the} second element 16 around a fixed central axis, and

e) the rotation of the second element 16.

The angular cycle T _{i of a} pair of female and male paired elements is given by the equation:

Where:

ω _f , ω _m — intrinsic angular velocities of the covering and covered elements around their own centers;

ω _I is the angular velocity of an independent element, for example, an element performing rotation, the angle of which determines the value of T _i ;

n _{m, f} is the order of symmetry,

n _{m, f} for the hypotrochoidal scheme with an external envelope, and n _f for an epitrochoidal scheme with an internal envelope.

Differential movement (containing the planetary movement of the elements 6 and 16 and the rotation of the elements 15, 15 'and 17, 17') in set 1 is determined by the following parameters:

и

и

and

and

The total volume of the working chambers 100, 300, controlling the rotation of the shaft 4, is set as V _{T (100)} = 6V ₁₀₀ 360/90 = 24V ₁₀₀ and V _{t (300)} = 6V ₃₀₀ 360/90 = 24V ₃₀₀ .

The total volume of the working chambers 200 and 400 during the rotation of the shaft 4 is set as V _{T (200)} = 5V ₂₀₀ 360/75 = 24V ₂₀₀ and V _{t (300)} = 5V ₃₀₀ 360/75 = 24V ₃₀₀ .

Turning now to the third set of 3, it should be noted that the differential motion with fixed elements 7 ', 17', the rotation of the elements 5, 15 or 5 ', 15' with the angular speed specified by the gearbox 18 from the shaft 4 (independent movement), and planetary the movement of the elements 6 ', 16' (dependent movement) is determined by the following parameters:

и

and

The total volume of the working chambers 100 'and 300' of set 3 during the rotation of the shaft 4 is set as

ω _{T (100 ')} = 6V _100' 2π / 3π = 4V _{100 '} and V _{T (300')} = 6V _{300 '} 2π / 3π = 4V _300' .

The total volume of the working chambers 200 'and 400' during the rotation of the shaft 4 is set as V _{T (200 ')} = 5V _200' 2π / 2,5π = 4V _{200 '} and V _{T (400')} = 5V _{400 '} 2π / 2, 5π = 4V _{400 '} .

From the above it is obvious that in the case of differential motion of the elements, the angular cycle can, according to the invention, be varied by changing the relative angular velocities of the movement of the screw elements forming the working chambers. The angular cycle can be 90 degrees in set 1, 360 degrees in set 2, 540 degrees in set 3. In other words, it can be reduced (thus compressing the working medium) and it can be increased (thus expanding the working medium according to the invention). Then the effectiveness of the method according to the invention can be improved.

The direction of the axial movement of the medium along the Z axis in the chambers 100, 200 and 300, 400 is determined by the direction of rotation of the centers O ₆ , O _{16 of the} elements 6, 16 in the set 1. As mentioned above, to select the same directions of movement of the medium, the same direction of rotation is set centers O ₆ , O ₁₆ . If you want to choose the opposite directions of movement of the working medium in the chambers 100, 200, on the one hand, and 300, 400 - on the other hand, the rotation of the centers O ₆ , O ₁₆ should be performed in opposite directions.

In the suction set 1 with compression, the compression is performed with the release (discharge) of the working substance into the mechanism 2. Due to the choice of different kinematic schemes 1 and 2, the values of the angular period of the axial movement of the working chambers, counted from the angle of rotation of the output link 4, are also different.

Set 1, consisting of groups of elements 5, 6, 7 and 15, 16 and 17, forms a suction and pre-compression section in which continuous cyclic stepwise air compression is performed. The group of elements 8 and 9 in set 2 provides the final compression and release (discharge) of the working medium. The working chambers 100, 200 of the suction in the differential mechanism 1 are formed by an outer group of mating elements 5, 6, 7, which are located coaxially with the eccentricity in the internal cavities of each other. Pre-compression is performed when air is pumped into the inner group of mating elements 15, 16, 17. The synchronizing device 11 serves to bring the rotor elements 5, 7 and 15, 17 in the set 1 into rotation in different directions with equal angular velocities, i.e. . with counter-rotation. At the same time, the shaft 4 of the rotor 9 in the set 2 is rotated. The final compression chambers 140 in the planetary mechanism 2 are formed by elements 8 and 9, where the element 9 is pivotally mounted for rotation by means of self-synchronization on the crank 10 of the shaft 4. The other element 8 is stationary.

The relationship of the rotational movements of the elements 5, 7 and 15, 17 in the set 1 and 9 in the set 2 with the rotational movements of the elements 5 'and 15' in the set 3 (pivotally mounted for rotation in the fixed housing 13) around the central axis Z is provided with a rigid mechanical connection of the elements 5 ', 15' with the shaft 4 in the set 3 by means of a synchronizing device 14 having a gear ratio 3, by articulating the element 9 with the shaft 4 in the set 2 and mechanically connecting the elements 5 and 15 (pivotally mounted for rotation in the fixed housing 13) in 1 with shaft 4 to redstvom synchronizing device 11, which is a rotation direction inverter having a gear ratio of -1. The element 8 (stator) in the set 2, the elements 7 ', 17' (the stators in the set 3) are mechanically rigidly connected to the fixed body 13. The mechanical connection of the elements 5 ', 15' in the set 3 (articulated for rotation in the fixed case 13) with the shaft 4 is performed by means of a synchronization device 14, which is a rotary motion reducer having a gear ratio 3.

In parallel with ensuring synchronization of rotation of elements inside differential mechanisms 1 and 3, synchronization of rotation between groups of differential and planetary mechanisms 1 and 3 is provided, on the one hand, and 2, on the other hand. You can also synchronize the rotation of the elements of the planetary and differential mechanisms by alternating the orders of symmetry of the elements of all groups 1, 3 or 2.

The choice of the number of transformation groups and the scheme of how planetary and differential kinematic mechanisms are combined is determined by the required angular factor and a combination of axial displacement periods in the working chambers between these mechanisms.

The operation of the engine shown in FIG. 1 is as follows: the gas component of the working substance of the engine (for example, air) is let into kit 1 through the open left end surface of elements 5, 6 and 7 (where arrows are shown in FIG. 1) first groups. Then it is served in the open left end surface of the elements 15, 16 and 17 of the second group through the channel (gap). The above-mentioned groups of elements 5, 6, 7 and 15, 16, 17 (together with elements 8, 9) form a rotary screw air compressor 1 of volumetric type. Through the channel in the shaft 4, compressed air is removed from the set 1 and fed into the open left end surface of the elements 8 and 9 of the set 2 of combustion, namely, into the combustion chamber 140. The compression ratio is 8 (V ₁₀₀ + V ₂₀₀ ) / V ₁₄₀ . Following the filling of the combustion chamber 140 with six volumes of air from the compressor 1 and its closure, the device 12 injects fuel into the chamber 140 and ignites it.

In the combustion cycle at constant pressure (as in the Diesel cycle), the chamber 140 can be formed in one period of the biotic movement of elements 8 and 9 and the ignition of the fuel can be performed due to air compression. In the combustion cycle at a constant volume (as in the Otto cycle), the chamber 140 can be formed in two periods of the biotative movement of elements 8 and 9, and the ignition of the fuel can be carried out by a spark plug. In addition, the ignited mixture of fuel and air is then taken away from the open end surface of the elements 8 and 9 for expansion in the expansion compartment 3 to the open lower end surface of the elements 15 ', 16', 17 'and 5', 6 ', 7' of set 3 .

Set 3 is an expanded rotary machine (expander) of volume type, in which the process of expansion of the combustible mixture performs work on the shaft 4 of the engine. If the combustible mixture is prepared, it is released from the upper end of set 3 (shown by arrows). When the shaft 4 rotates, the mating elements 5, 6, 7, 15, 16 and 17 in the set 1 limit and move the working medium of the suction compartment 1 (6 chambers between the elements 5, 6 and 15, 16 and 5 of the chambers between the elements 6, 7 and 16, 17 along the Z axis) by moving their contact interface portions to two independent degrees of freedom of the rotational movement of the elements 5, 7, 15, 17 in the set 1 in the opposite direction, as determined by the node 11.

When the shaft 4 rotates, the mating elements 8 and 9 in the set 2 limit and move the three working chambers 140 of the combustion compartment 2 along the Z axis by moving their contact mating sections by one independent degree of freedom of the rotational movement of the elements 9 in the set 2 using the crank of the shaft 4.

When the shaft 4 rotates, the mating elements 5 ', 6', 7 ', 15', 16 ', 17' in the set 3 limit and move the working chambers of the expansion and outlet compartments 3 (6 chambers between the elements 5 ', 6', 15 ' , 16 'and 5 chambers between elements 6', 7 ', 16', 17 'in each group) along the Z axis by moving their contact interface sections with one independent degree of freedom of the rotational movement of elements 6', 16 'in set 3. Full cycle the axial movement of the working chambers between the elements 5 ', 6', 7 ', 15', 16 ', 17' for one revolution of the shaft 4 in set 1 occurs four times per revolution of the shaft 4. In other words,

[4 (V _{100 ′} + V _{200 ′} )] / [4 (V _{300 ′} + V _{400 ′} )] × [4 (V _{300 ′} + V _{400 ′} )] / 3V ₁₄₀ = [4 (V _{100 ′} + V _{200 ′} )] / 3V ₁₄₀ .

Interconnected rotational movements around the main axis Z of the machine and around their own axes occur in all sets 1-3 with three degrees of freedom of mechanical rotation.

In the engine shown in FIG. 1, mechanically coupled rotors 5, 15 and mechanically coupled counter-rotors 7 and 17 simultaneously rotate around the Z axis in opposite directions with the same relative speeds ω _{(5, 15)} = -1 and ω _{(7, 17)} = 1. The relative angular velocity ω _{re of the} line of the O ₆ -O-O ₁₆ centers of the rotors 6 around the Z axis relative to the speed of the rotors 5, 7 is set as ω _re = 5, while the relative angular velocity ω _{s (6,16) of} the satellite rotors 6, 16 around their axes O ₆ , O _{16 is} given as ω _{s (6,16)} = 0.2.

The compression ratio k ₁ in set 1 is defined as the ratio of the sum of the products of the total volume of six chambers between elements 5, 6 and the total volume of five chambers between elements 6, 7 to the sum of the products of the total volume of six chambers between elements 15, 16 and the total volume of five chambers between elements 16, 17, multiplied by the number of cycles of volume change per revolution of the shaft 4, namely:

k ₁ = 24 (V ₁₀₀ + V ₂₀₀ ) / [24 (V ₃₀₀ + V ₄₀₀ )] = (V ₁₀₀ + V ₂₀₀ ) / 2 (V ₃₀₀ + V ₄₀₀ ).

The compression ratio k ₂ in set 2 is defined as the ratio of the sum of the products to the product, i.e. the first product of the full volume of six chambers between elements 15 and 16 in set 1 and the second product of the full volume of five chambers between elements 16 and 17 in set 1 to the product of the total volume of three combustion chambers between elements 8 and 9 in set 2 for one revolution of the shaft 4, namely:

k ₂ = 24 (V ₃₀₀ + V ₄₀₀ ) / 3V ₁₄₀ = 8 (V ₃₀₀ + V ₄₀₀ ) / V ₁₄₀ .

The total compression ratio k of the engine is equal to the product of the compression ratios in sets 1 and 2,

k = k ₁ k ₂ = 8 (V ₁₀₀ + V ₂₀₀ ) / V ₁₄₀ .

It is possible to obtain any compression ratio in the chamber 140 for the purposes of the present invention, which is required in various engines, by choosing the appropriate ratios of the geometric volumes of the chambers in sets 1 and 2. It is also possible to provide any compression mode, adiabatic or polytropic compression mode. The implementation of the chamber 140 of the two periods of the biotative movement of the elements 8 and 9 allows the mixture to be burned from fuel and air with the axial transfer of gas from one chamber to another with a constant volume. Thus, the thermodynamic efficiency of the engine is increased.

The work of the exhaust kit 3 occurs with the fixed elements 7 ', 17'. All mating elements 5 ', 6', 7 ', 15', 17 'together limit the working chambers of the exhaust compartment of the machine and move them along the Z axis by the movement of their contact mating portions.

The mechanism of set 3 is reversible.

The degree of expansion of the working substance in set 3 is set by the geometric parameters of the conjugated elements and the number of stages of expansion. For the purposes of the present invention, it can be selected in such a way as to ensure complete expansion of the working substance, while reducing its pressure to atmospheric pressure. Thus, no acoustic noise is generated. In this case, the mechanical energy provided by the working substance is fully used to rotate the shaft 4.

In some other cases, in particular when driving a vehicle with a falling moment characteristic, it is useful to use only some of the mechanical energy in set 3 and use the remaining part of the mechanical energy in an additional volumetric expansion machine 33 (expander similar to expander 3), which is illustrated dashed line in figure 1. Its shaft 34 (also shown by dashed lines in FIG. 1) does not have a mechanical connection with the shaft 4. The mechanical energy of rotation is removed from the output shaft 34 of the additional machine 33 according to the engine diagram with two shafts.

In another alternative embodiment, it is possible to use the jet ejection of combustion products from the output element of the compartment 3 according to the scheme of the air-jet engine, in which the compressor using the method according to the present invention is formed by compartments 1 and 2, and in which the expander using the method according to the present invention is formed compartment 3 of a rotary screw machine of a volume type, in which the combustion of fuel can occur in the chambers 140 of set 2 with a constant volume, thereby increasing the engine power I am. Fuel combustion can also be performed in external combustion chambers (not shown) that are connected to chambers 140.

In addition, in order to use not only the mechanical energy of the working substance, but also (fully) use the thermal energy, it is possible to ensure the release of hot gases in a special heat exchanger (which is not shown in FIG. 1) in order to heat the air that passes through it from set 1 into set 2 with a constant volume, thereby increasing its pressure. Therefore, according to the invention, it is possible to fully utilize the thermal and mechanical energy of the working substance in the engine and increase its efficiency, while ensuring silent operation at atmospheric pressure and temperature of the exhaust gases.

Rotation in opposite directions of the output shafts 4 and 5 in the compartment 1, which is set by the inverter 11, allows the engine to be connected to devices rotating in the opposite direction, such as propellers or propellers, rotating elements of mowers, saws, crushers, etc. .d. The connection can also be made with an opposite rotating turbine or aircraft propellers, etc.

When using a volumetric screw machine, this method allows synchronous and simultaneous conversion of the movement of the conjugated elements when passing the working substance through the differential kinematic mechanism in set 1.

Claims (7)

1. A method of energy conversion in a rotary screw machine, which contains a first set of conjugated male and female elements (5, 6, 7; 15, 16, 17) and at least a second set of conjugated male and female elements (8, 9; 5 ', 6', 7 '; 15', 16 ', 17'), spaced from the first set (1) along the central axis of the machine, with the covering elements (5, 6, 15, 16; 8; 5 ', 6' , 15 ', 16') of each set have an internal profile surface (105, 106, 115, 116; 108; 105 ', 106', 115 ', 116'), centered on the first longitudinal axis (Z), covered elements (6 , 7, 16, 17; 9; 6 ', 7', 16 ', 17') ka Each set (1, 2, 3) has external profile surfaces (206, 207, 216, 217; 209; 206 ', 207', 216 ', 217'), centered on the second longitudinal axis, the first and second axes are parallel to each other , and the male elements are placed in the cavity of the corresponding female elements, in which, with the rotational movement of the male and / or female elements, working chambers are formed between the female and male elements, performing axial movement, and the rotational movements of different sets (1, 2, 3) are synchronized in this way that synchronous and sif Noe motion elements of different sets (1, 2, 3) operate with different values of the angular periods of the oscillations of axial movement of the working chambers. 2. The method according to claim 1, wherein the angular period is reduced from one set to the next set, thereby compressing the working environment. 3. The method according to claim 1, wherein the angular period is increased from one set to the next set, thus expanding the working environment. 4. The method according to claim 1, in which a hollow shaft (4) and a working medium passing through it are used as a means of synchronizing the rotational movements of different sets (1, 2, 3). 5. The method according to claim 1, wherein the first set (1) forms a differential kinematic mechanism having three degrees of freedom of mechanical rotation, of which two degrees of freedom are independent, and the second set (2) forms a planetary kinematic mechanism having two degrees of freedom mechanical rotation, of which one degree of freedom is independent. 6. The method according to claim 1, in which thermal energy of the working medium is removed and fed to the heat exchanger. 7. The method according to claim 1, wherein the mechanical energy generated in one of these sets is used to propel another device.

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