CN1910342A - Energy transformation method for volumetric type rotating screw machine - Google Patents

Abstract

A method of transforming energy in a rotary screw machine that comprises a first and a second set of conjugated male and female elements spaced apart from each other along a central axis and having inner/outer profiled surfaces. Upon rotary motion of the male and/or female elements, working chambers are formed between these elements. The working chambers perform an axial movement. The rotary motions of the different sets (1, 2, 3) are synchronized in such a manner that synchronous and inphase motion of the elements in the different sets is performed with different values of angular periods of oscillation of axial movement of the working chambers. Thereby, a working medium transported in these working chambers can be compressed or expanded.

Description

Energy Conversion Method in Volumetric Rotary Screw Machine

technical field

The invention relates to a method of energy conversion for use in a rotary screw machine.

Background technique

A volume screw machine of the rotary type includes mating screw elements, namely a female (surrounding) screw element and a male (surrounded) screw element. The female screw element has an inner contoured surface (internal helicoid, concave) and the male helical element has an outer contoured surface (outer helicoid, convex). The helicoid is non-cylindrical and constrains the element radially. They are each centered on mutually parallel but usually non-coincident axes spaced apart by a length E (eccentricity).

From US 5439359 is known a type of three-dimensional rotary screw machine in which a male element surrounded by a fixed female element makes a planetary movement relative to said female element.

The working chamber of the internally cooperating rotary positive displacement screw machine is formed by a kinematic mechanism consisting of these male and female curved elements.

The conversion of motion is based on the associated rotational movement of the male and female elements, whereby mechanical curvilinear contact can be made with each other and these closed working chambers can be formed for the working substance, said working chambers undergoing axial movement (axis to move).

In most cases, the helicoid has the shape of a cycloid (trochoid) as known, for example, from French patents FR-A-997957 and US3975120. The motion conversion used in electric motors has been described by V. Tiraspolskyi in the section "Hydraulical Downhole Motors in Drilling" of "The Course of Drilling", pp. 258-259, Edition TECHNIP, Paris.

The effectiveness of prior art energy conversion methods in screw machines is determined by the intensity of the thermodynamic processes taking place in the screw machine and is characterized by a generalized parameter "angular period". Said angular period is equal to the rotation angle of any rotary element (male, female or synchronous connection part) selected as an element with independent degrees of freedom.

The angular period is equal to the rotation angle of the element with independent degrees of freedom, and the rotation angle corresponds to the total period of change of the cross-sectional area (opening and closing) of the working chamber formed by the male and female elements, which corresponds to The working chamber moves axially for one period P _m in a screw machine with a helicoid, and corresponds to one period P _f for the axial movement of the working chamber in a screw machine with an outer helicoid.

Existing methods of energy conversion in rotary positive displacement screw machines with mating elements of curved shape, also implemented in similar positive displacement rotary machines, have the following disadvantages:

- technical potential is limited due to flaws in the process of tissue movement, so that each rotation of the drive with independent degrees of freedom does not increase the number of angular cycles;

- will limit the power coefficient of similar screw machines;

- would limit efficiency; and

- There will be a reaction force on the fixed body of the screw machine.

In all cases, the longitudinal axes of the inner cooperating helical elements are parallel. Sometimes they have an eccentricity and some of the longitudinal axes are movable. Available with planetary or differential motion.

Contents of the invention

The object of the present invention is to solve the above-mentioned problems.

The positive displacement screw machine used in the present invention comprises at least two sets of male and female (male, female) cooperating elements, which are preferably spaced apart from each other along the central axis of the screw machine. Each group of female elements has an inner contour surface centered on the first longitudinal axis, and each group of male elements has an outer contour surface centered on the second longitudinal axis. The first and second longitudinal axes are parallel to each other. The male elements are placed in the lumens of the corresponding female elements.

In the method of energy conversion in a rotary screw machine according to the present invention, when the male and/or female elements are rotationally moved, the working chamber formed between the female and male elements is axially moved. In the present invention, the rotational movements of the different groups are synchronized in such a way that the angular periods of oscillation of axial movement of the working chambers have different values. Synchronous in-phase movement between elements.

In other words, the parts (or elements) of said screw machine are arranged in such a way that when one cooperating element moves, the coaxial longitudinal axes in each set move at angular velocities with predetermined ratio characteristic values (one relative to the other) move.

Synchronization helps to optimize the function of the screw machine.

In a preferred embodiment of the invention, the angular period decreases from one group to the next so that the working medium can be compressed. In an alternative embodiment, the angular period increases from one set to the next so that the working medium can be expanded.

An embodiment of the screw machine comprises a rotor and a counter-rotor, wherein the latter counter-rotates relative to the rotor. Planetary motion elements can be placed between them. Said embodiment facilitates a stable and balanced movement of the working medium in the working chamber.

The coupling device may be a mechanical device. As an alternative, the working medium can be used to couple different groups. In a combination of these alternatives, the synchronization device comprises an (at least partially) hollow shaft, wherein the working medium passes through the shaft.

In another preferred embodiment, a first group forming a differential motion mechanism and a second group forming a planetary motion mechanism are used, wherein the differential motion mechanism has three mechanical rotational degrees of freedom, two of which are independent Yes, the planetary motion mechanism has two mechanical rotational degrees of freedom, one of which is independent. A third set of cooperating elements may form a differential motion mechanism.

The screws can now be arranged in such a way that the cooperating elements in the first and third groups have approximately the same cross-section. In other words, the first and third groups can be of the same design and then coupled by means of the second group. In particular, the average radius and/or thickness and/or undulations of the helical elements are equal.

Of course, the set may comprise more than a single male and female element. In a preferred embodiment, there is a nested structure. For example, the aforementioned first and third groups may comprise two sets of male and female cooperating elements separated by a channel through which said working medium can be transmitted.

In another preferred embodiment of the method according to the invention, the working medium can be extracted and supplied with thermal energy in a heat exchanger (extracted from the working medium in the first stage and passed through in the second stage to its supply passes from there, or vice versa).

Also, the mechanical energy generated in one of the groups can be used to drive another mechanical device. In other words, mechanical energy can be extracted from the rotating screw machine. Of course, the well-known laws of thermodynamics must be obeyed, especially in certain parts of the screw machine or in the working medium that temperature changes must occur simultaneously.

Description of drawings

Below, a preferred manner of implementing the present invention is described with reference to the accompanying drawings, which can make the present invention more obvious. The accompanying drawings include:

Figure 1a shows a longitudinal section view of a volumetric screw machine used in the present invention;

Figure 1b shows a schematic diagram of the positive displacement screw machine in Figure 1a;

Figure 2 shows a cross-sectional view of the positive displacement screw machine of Figure 1 taken along line II-II in Figure 1a;

Figure 3 shows a cross-sectional view of the positive displacement screw machine shown in Figure 1a taken along line III-III in Figure 1a;

Figure 4 shows the principle of how to design the end profile of the helicoid of any one mating element; and

FIG. 5 shows the electronic CAD structure of the helicoid of the mating element of symmetry order n _m =4.

Detailed ways

The volumetric screw machine used in the present invention shown in Figures 1a and 1b comprises three different sets of cooperating elements, namely a first set 1, a second set 2 and a third set 3, wherein said first set 1 forms Differential motion for sucking and compressing air, said second group 2 forming planetary motion for compressing air (and for providing combustion of fuel in its chamber 140), said third group 3 for A differential motion mechanism that expands the fuel product of the bank 2 chambers 140 .

In other words, the positive displacement screw machine used in the present invention is a rotary screw internal combustion engine in which motion produces conversion and a continuous cyclic change of working substance energy is synchronized with the process of passing the working substance through different groups of working chambers conduct. The positive displacement screw machine can thus generate working mass energy. There are two synchronization devices 11 and 14, which are used to support the operation of Group 1 and Group 3 respectively. They can be provided as a single element as shown in Figure 1b.

It should be noted that the different groups 1 , 2 and 3 of said positive displacement screw machines according to the invention are arranged apart from each other along the central axis Z of the screw machine. In other words, groups 1, 2 and 3 do not form an enclosure with each other. Rather, they are placed one behind the other, or, in other words, they are arranged one behind the other. They are all centered on said central axis of the screw machine.

The different groups are coupled by the action of the mechanical link and the gaseous working substance, the gas link. The mechanical link between groups 1 , 2 and 3 is provided by a common shaft 4 which is partly hollow and also provided with a crank 10 connected thereto. Air can pass from group 1 into group 2 through the hollow part of shaft 4 . Groups 1 and 2 together form a positive displacement rotary screw compressor (compressor). Group 2 provides the combustion chamber 140, and groups 2 and 3 cooperate to form a volumetric rotary screw expander (expander).

The first and third sets 1 and 3 respectively comprise two sets of mating elements, the first set consisting of elements 5, 6 and 7 (5', 6' and 7') and the set consisting of elements 15, 16 and 17 (15' , 16' and 17') the second set.

It should be noted that the first group 1 and the third group 3 have substantially the same shape, ie have the same cross-section. Especially in the case of individual helical elements, they have the same average radius and the same thickness.

The details are as follows:

The first group comprises first female elements 5 and 15 having inner contour surfaces 105 and 115 respectively, and these female elements 5 and 15 are centered on a fixed central axis Z which is the axis of symmetry of said positive displacement screw machine. Both female elements 5 and 15 have a symmetry level of 6. In the following, the term "symmetry order" denotes the rotational symmetry of the end faces of these elements. The first group also includes second elements 6 and 16, which are both male and female elements, ie include respective outer trochoidal surfaces 216, 116 and inner trochoidal surfaces 206, 106, respectively. Their symmetry order is 5 and are centered on their own axes O ₆ and O ₁₆ respectively. They perform planetary motion. Synchronizing elements 7 and 17 are also provided, which have outer contour surfaces 207 and 217 respectively and have a symmetry level of four. Between these elements, studios 100, 300 and studios 200 and 400 are provided. Channels are provided between elements 5, 6 and 7 and between 15, 16 and 17 so that the air conveyed in the working chambers 100 and 200 can be returned under (in Figure 1a) the positive displacement screw machine side, which can then also be transported in the studios 300 and 400.

The second group 2 consists of only two mating elements, namely a female element 8 and a male element, wherein the female element 8 has an inner profile surface 108 and has a degree of symmetry of 3 and is also centered on the axis Z, said male element Has an outer concave trochoidal surface 209, and has a symmetry of order 2, and is centered on the axis O ₉ while performing a planetary motion. A combustion chamber (working chamber) 140 is formed between these elements. Fuel can enter these combustion chambers 140 by means of the nozzles 12 .

Each set of mating elements of the third group 3 includes first male elements 7' and 17' respectively, which have outer surfaces 207' and 217' respectively, and are of symmetry order 4 and centered on the fixed central axis Z. The second elements 6' and 16' are both male and female elements comprising respective initial trochoidal surfaces 106', 206' and 116', 216' respectively, both having a symmetry order of five. These second elements 6' and 16' are respectively centered on a second axis O6 _' , _O16' and perform a planetary movement. Elements 5' and 15' of symmetry level 6 with inner surfaces 105' and 115' respectively act as synchronizing elements. Between these elements, a working chamber 100', 300' and a working chamber 200', 400' are formed.

The elements 5 , 6 , 7 and 15 , 16 , 17 forming group 1 of the differential kinematics shown in FIG. 1 a have three mechanical rotational degrees of freedom. Two of these degrees of freedom are independent rotational degrees of freedom.

The same is true for the elements 5', 6', 7' and 15', 16' and 17' of group 3 forming the differential kinematics.

The element 9 of the planetary motion mechanism translating the motion of the group 2 shown in FIG. 1 a has two mechanical rotational degrees of freedom. One of the degrees of freedom is an independent rotational degree of freedom.

In the present invention, energy conversion is achieved by converting the movement of said cooperating elements in the form of mechanically linked movements of sets of elements of sets of kinematic mechanisms that are formed by interacting with each other in their inner cavities. The kinematic mechanism formed by the matching elements 5, 6, 7, 15, 16, 17 and 8, 9 arranged coaxially at the eccentric point. Furthermore, the cranks 10 can also be used as synchronizing means 11 for the synchronous associated movement of said elements around the main shaft of the screw machine and their own axes. For this purpose, at least in two sets of kinematic mechanisms, the movement conversion takes place synchronously, wherein the movement of the mating elements is converted to receive the energy of the working substance.

The method according to the invention facilitates the synchronization and simultaneous execution of the transformation of motion of the cooperating elements, while the working substance passes through the differential kinematics in group 1, which are mechanically connected to each other and as shown in FIG. 1 a form for example Suction and compression section. At least said differential motion mechanism formed in group 1 has three mechanical rotational degrees of freedom, two of which are independent, and the planetary motion mechanism of group 2 shown in Figure 1a includes the compression and discharge of the working substance part, the planetary motion mechanism has an independent rotational degree of freedom, wherein, in the differential motion and the planetary motion mechanism, different values are provided for the angular period of the axial movement of the working chamber (when the slave shaft 4 when calculating the rotation angle).

It should be noted that the helical element cannot be of arbitrary shape but must have well-defined characteristics. Their well-defined shape profile D _m constructed in the following way will be described below with reference to FIG. 4 , wherein the degree of symmetry of the profile D _m is n _m =5:

First, start the description with the construction of a hypocycloid Γ with the following parametric form (depending on the parameter t):

x(t)=E cos(n _m -1)t+E(n _m -1)cos t

y(t)=E sin(n _m -1)tE(n _m -1)sin t

This hypocycloid Γ of symmetry order n _m , (n _m +1), (n _m +2)...(n _m +i) is such a curve that the radius is O ₁ A=E and the center is O A point A on the circle of _E lies along the circle with a radius equal to En _m , E(n _m +1), E(n _m +2) ... E(n _m +i) and centered at O _m (as The curve drawn when the inner surface of another circle (shown in Figure 1a) rolls (without sliding). The points where point A touches these circles are designated with reference signs B, C, D, F, I. An equivalent construction method of this hypocycloid Γ with symmetry order n _m , (n _m +1), (n _m +2)...(n _m +i) is based on having radius E(n _m -1) , E(n _m +1)...E(n _m +1+i) and a point A on a circle whose center is O ₂ has a relationship with En _m , E(n _m +1), E(n _m +2)…E(n _m +2+i) The curve drawn when the inner surface of a circle of equal radius rolls (without sliding).

The profile D _m used for the helical element in the present invention starts from the hypocycloid Γ, and the profile D _m is obtained by placing a circle with a radius r ₀ , for example equal to 2E in FIG. 4 , ie r ₀ =FR = 2E along Hypocycloid Γ rolling is obtained, wherein, during rolling, the center of the circle moves along the hypocycloid.

If r ₀ is chosen to vary monotonically along the z-axis (the axis perpendicular to the plot in Fig. 4), a profile D _m is obtained that satisfies the following parametric equation (depending on the parameter t):

x(t)＝E<cos[(n/(n+1))[arcsin(sint)-t]]+ncos[(arcsin(sint)-t)/(n+1)>+r ₀ (z )cos[arcsin(sint)-(arcsin(sint)-t)/(n+1)];

y(t)＝E<sin[(n/(n+1))[arcsin(sint)-t]]+nsin[(arcsin(sint)-t)/(n+1)>+r ₀ (z )sin[arcsin(sint)-(arcsin(sint)-t)/(n+1)];

Wherein, n=n _m -1 or n=n _f -1.

FIG. 5 shows a three-dimensional representation of a helical element obtained by the construction described above.

All outer surfaces 217, 216, 207, 206, 217', 216', 207', 206', 209 of respective male elements 17, 16, 7, 6, 17', 16', 7', 6' and 9 and all inner surfaces 105, 106, 115, 116, 105', 106', 115', 116', 108 are radially bounded by such non-cylindrical helical surfaces configured in the manner described above. It should be noted that the degree of symmetry of these surfaces increases from the inside to the outside. In the second group, the helical element 9 has a symmetry order of 2 and the helical element 8 has a symmetry order of 3. In the first group 1 and the third group 3, the innermost elements 17, 17' have a degree of symmetry of 4, which are respectively surrounded by elements 16, 16' of degree of symmetry 5, and the elements 16, 16' themselves have Each is surrounded by an element 15 , 15 ′ having a symmetry level of 6 and each having an inner contour surface 115 , 115 ′. This series of levels of symmetry starts with elements 7, 7' and repeats with elements 5, 5'.

The elements 5 , 7 , 15 , 17 , 5 ′, 7 ′, 15 ′, 17 ′ are arranged in such a way that they are rotatable about the axis Z. The axes O6, O16, O6', O16', O9 of the respective elements ₆ , ₁₆ , _6' , _16' and ₉ are movable. It should be noted that the eccentricity of the axis O ₆ relative to the central axis Z is E ₁ =E, and the eccentricity of the axis O ₁₆ relative to the central axis Z is -E ₂ (less than E ₁ ). These axes O ₆ and O ₁₆ are placed on a line transverse to said central axis. During rotation, their spatial relationship remains unchanged. In other words, if the eccentricity is chosen in such a way that a statically balanced positive displacement screw machine is obtained, said screw machine can also be dynamically balanced. The elements 6 , 16 and 9 are arranged in the screw machine in such a way that they can perform a planetary movement about the central axis Z. Elements 6, 16, 6', 16' are arranged respectively between elements 5, 7; 15, 17; 5', 7' and 15', 17' without any additional means to start the rotor into planetary motion. Element 9 as rotor is articulated on crank 10 of shaft 4 .

In groups 1 and 3 as differential motion mechanisms and in group 2 as planetary motion mechanisms, the connecting parts are arranged in such a way that in group 1 a continuous cycle of suction and compression of volume is achieved, in the combustion chamber of group 2 Compression and release of the working substance in 140 and expansion of said working substance and working chambers 100 ′, 200 ′, 300 ′ and 400 ′ in group 3 . It should be noted that the combustion section with the combustion chamber 140 is formed by elements of group 2 as a planetary motion mechanism, the cross-section of which is shown in FIG. 3 . Group 2 as planetary motion mechanism consists of element 8 as central stationary stator, element 9 as planetary rotor-satellite and crank 10 on shaft 4 . The nozzle 12 is used to inject fuel into the combustion chamber 140 and to ignite the fuel. The combustion chamber 140 may be formed by one and two torsional periodic profiles of the elements 8 and 9 (for fuel combustion at constant volume).

In the case of a fixed element 8, the planetary movement of the element 9 is defined by the following parameters:

ω ₈ =0, symmetric order n ₈ =3; n ₉ =2; ω ₁ =ω _{revolution (9)} =1; ω ₉ =ω _{rotation (9)} =-0.5. The total volume in group 2 due to the rotation of shaft 4 is V ₂ =(3·V ₁₄₀ ·360/360)=3V ₁₄₀ . In each group, the element 8, being a female screw element, is rotatable about said central axis. As an alternative, the element 8 can also be stationary. The planetary movement of the element 9 as a male helical element cooperating with the first element 8 can be performed with the help of a synchronized crank 10 or a third (male) cooperating helical element coaxial with the first element.

Returning now to the first group, one can choose the first set of elements 5, 6 and 7 in three states:

a) rotation of the first element 5 around said fixed central axis (stationary state) and rotation of the third element (synchronizing element) 7 around said fixed central axis (stationary state),

b) the revolution of the axis O6 of the second element ₆ around said fixed central axis, and

c) Rotation of the second element 6 with the aid of a synchronous coupling part (male cooperating helical element 7 ) coaxial with the first element 5 .

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

d) rotation of the first element 15 around said fixed central axis (stationary state) and rotation of the third element (synchronizing element) 17 around said fixed central axis,

e) revolution of the axis O ₁₆ of the second element 16 around said fixed central axis, and

f) The rotation of the second element 16 .

The angular period T _i of a pair of female-male mating elements is given by the following equation:

${\mathrm{<span\; class="notranslate">\; T</span>}}_{\mathrm{<span\; class="notranslate">\; i</span>}}<span\; class="notranslate">\; =</span>\frac{\mathrm{<span\; class="notranslate">\; 2</span>}\mathrm{<span\; class="notranslate">\; \&pi;</span>}}{{\mathrm{<span\; class="notranslate">\; no</span>}}_{\mathrm{<span\; class="notranslate">\; m</span>}<span\; class="notranslate">\; ,</span>\mathrm{<span\; class="notranslate">\; f</span>}}<span\; class="notranslate">\; |</span><span\; class="notranslate">\; (</span>{\mathrm{<span\; class="notranslate">\; \&omega;</span>}}_{\mathrm{<span\; class="notranslate">\; f</span>}}<span\; class="notranslate">\; /</span>{\mathrm{<span\; class="notranslate">\; \&omega;</span>}}_{\mathrm{<span\; class="notranslate">\; I</span>}}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; (</span>{\mathrm{<span\; class="notranslate">\; \&omega;</span>}}_{\mathrm{<span\; class="notranslate">\; m</span>}}<span\; class="notranslate">\; /</span>{\mathrm{<span\; class="notranslate">\; \&omega;</span>}}_{\mathrm{<span\; class="notranslate">\; I</span>}}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; |</span>}$

in:

ω _f , ω _m - the respective angular velocities of the female and male components around their respective centers;

ω _I - the angular velocity of an independent element, such as an element performing a revolution, the angle of rotation of which defines the value of _T ;

n _{m, f} - symmetric order,

n _m,f - corresponds to an inner trochoid design with an outer envelope, n _f corresponds to an outer trochoid design with an inner envelope.

The differential motion in group 1 (including planetary motion of elements 6, 16 and rotation of elements 15, 15 and 17, 17) is defined by the following parameters:

ω _{ro(5, 15)} = 1; ω _{ro(7, 17)} = -1; (ω _{ro(7, 17) -} ω _{re(6, 16)} )/(ω _{ro(5, 15) -} ω _{re (6,16)} )=n _5,15 /n _7,17 and ω _{re(O-6), (O-16)} =(ω _ro(5,15) n _5,15 -ω _{ro(7,17 )} n _7,17 )/(n _5,15 -n _7,17 )=(6+4)/(6-4)=5; (ω _s(6,16) -ω _re(6,16) ) /(ω _ro(5,15) -ω _re(6,16) )=n _5,15 /n _6,16 and ω _m(6,16) =ω _s(6,16) =(ω _{ro(5 , 15)} −ω _re(6,16) )(n _5,15 /n _6,16 )+ω _ro(6,16) =(1−5)(6/5)+5=0.2.

The total volume of the working chambers 100, 300 in which the drive shaft 4 rotates is given by 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 given by V _{T(200 )} = 5V ₂₀₀ x 360/75 = 24V ₂₀₀ and V _{T(300 )} = 5V ₃₀₀ x 360/75 = 24V ₃₀₀ .

Returning now to the third group 3, it should be pointed out that with fixed elements 7', 17' differential movement, elements 5, 15' or 5', 15' are given after reduction of shaft 4 by reducer 18 The rotation (independent movement) at a given angular velocity and the planetary movement (dependent movement) of the elements 6', 16' is defined by the following parameters:

ω _{5', 15'} = ω _{ro(5', 15')} = 1/3; ω _{ro(7', 17')} = 0; ω _{re(O-6', O-16'} ) = (ω _{ro (5', 15'} )n _{5', 15'} )/(n _{5', 15'} -n _{7', 17'} )=2/(6-4)=1, and ω _{s(6', 16' )} = (ω _{re(5', 15')} -ω _{re(6', 16')} )/(n _{5', 15'} /n _{6', 16'} )+ω _{re(6', 16')} = (1/3-1)(6/5)+1=0.2.

The total volume of the working chambers 100' and 300' of the group 3 during the rotation of the shaft 4 is V _T(100') = 6V _100' × 2π/3π = 4V _100' and V _T(300') = 6V _300' ×2π/3π=4V _300' gives.

The total volume of the working chambers 200' and 400' during the rotation of the shaft 4 is V _T(200') = 5V _200' × 2π/2.5π = 4V _200' and V _T(400') = 5V _400' × 2π /2.5π=4V _400' gives.

From the above, it is evident that in the case of differential motion of said elements, according to the invention, the angular period can be varied by varying the relative angular velocity of the motion of the helical elements forming the working chamber. The angular period may be 90 degrees in group 1, 360 degrees in group 2, and 540 degrees in group 3. In other words, the angular period can be decreased (thus compressing the working medium) and it can be increased (thus expanding the working medium according to the invention). In this way, the efficiency of the method according to the invention can be increased.

The direction of axial movement of the working medium along the Z axis in the chambers 100 , 200 and 300 , 400 is defined by the direction of revolution of the centers O ₆ , O 16 of the elements 6 , ₁₆ in group 1 . As mentioned above, in order to select the same moving direction of the working medium, the revolutions of the centers O ₆ and O ₁₆ are performed in the same direction. If it is desired to choose the opposite movement direction of the working medium in the working chambers 100, 200 and in the working chambers 300, 400, the revolutions of the centers O ₆ , O ₁₆ should be reversed.

In suction group 1 with compression, compression is performed and the working substance is released (ejected) into group 2 . Due to the choice of different groups 1 and 2, the value of the angular period of the axial movement of the working chamber calculated from the angle of rotation of the shaft 4 is also different.

Group 1 consisting of two sets of elements 5, 6, 7 and 15, 16, 17 forms a suction and preliminary compression section, in which a continuous cycle of staged air compression is performed. A set of elements 8 and 9 in group 2 ensures the final compression and release (injection) of the working substance. The suction working chambers 100 , 200 in group 1 as differential kinematics are formed by an outer set of cooperating elements 5 , 6 , 7 arranged coaxially with eccentric points in each other's cavities. Preliminary compression is performed when air is pumped into the inner set of mating elements 15, 16, 17. The synchronizing device 11 is used to drive the elements 5, 7 and 15, 17 as rotors in the set 1 so that they rotate at the same angular speed in different directions, ie opposite directions. At the same time, the shaft 4 of the element 9 of the set 2 as rotor is driven in rotation. The last compressed chamber 140 in group 2 as a planetary motion mechanism is formed by elements 8 and 9 , wherein element 9 is articulated to rotate by self-synchronization on crank 10 of shaft 4 . Another element 8 is fixed.

The rotational movement of elements 5, 7 and 15, 17 in group 1 and element 9 in group 2 is related to the rotational movement of elements 5' and 15' in group 3 (articulated so as to be rotatable in a fixed body 13) about the central axis Z The associated transmission relationship between the rotary motions of is ensured in that in group 3 the elements 5, 15' are mechanically rigidly connected to the shaft 4 by means of a synchronizer 14 with a transmission ratio of 3, in group 2 The element 9 is articulated to the shaft 4, and the elements 5 and 15 (articulated to rotate in a fixed body 13) are connected in group 1 by a synchronization device 11 acting as a converter of the direction of rotation with a transmission ratio of -1 Mechanically connected to axis 4. The element 8 (stator) of group 2 and the elements 7' and 17' (stator) of group 3 are mechanically rigidly connected to the fixed body 13 . The mechanical connection of the elements 5', 15' of group 3 (articulated for rotation in a fixed body 13) to the shaft 4 is achieved by means of a synchronizer 14 as a rotary motion reducer with a transmission ratio of 3.

Synchronization of rotation between groups 1, 3 as a differential motion mechanism and group 2 as a planetary motion mechanism is also ensured while providing synchronization for the rotation of the elements inside groups 1 and 3 as a differential motion mechanism . It is also possible to synchronize the rotation of the elements of the planetary and differential kinematics by varying the order of symmetry of all sets of elements in groups 1, 3 or 2.

The selection of the number of switching groups and the scheme of how the planetary and differential motion mechanisms are combined is determined by the combination of the required angular range and the value of the axial movement period of the working chamber in these mechanisms.

The operation of said internal combustion engine shown in FIG. 1 a is as follows: the gaseous components of the working substance (for example, air) of the internal combustion engine pass through the left open end faces of the first set of elements 5, 6 and 7 (indicated by the arrows in FIG. 1 a) into group 1. It is then fed to the left open end face of the second set of elements 15, 16, 17 by means of a channel (gap). The aforementioned two sets of elements 5 , 6 , 7 and 15 , 16 , 17 (together with elements 8 , 9 ) form a volumetric rotary screw air compressor 1 . Through channels in the shaft 4 the compressed air is guided out of the group 1 and delivered to the left open end faces of the elements 8 and 9 of the combustion group 2 , ie into the combustion chamber 140 . The compression ratio is 8(V ₁₀₀ +V ₂₀₀ )/V ₁₄₀ . After that, the combustion chamber 140 is filled with six times the volume of air from the compressor 1 and closed, and the nozzle 12 injects fuel into the combustion chamber 140 and ignites it.

In a constant pressure combustion cycle (which is a Diesel cycle), chamber 140 can be formed in one twisting cycle of elements 8 and 9 and fuel can be ignited due to air compression. In a constant volume combustion cycle (which is an Otto cycle), chamber 140 can be formed in two twisting cycles of elements 8 and 9 and fuel ignition can occur due to ignition of the spark plug. Moreover, the ignited fuel-air mixture is then directed away from the open end faces of the elements 8 and 9 while expanding into the group 3 as an expansion, whereby the elements 15, 16, 17 and 5, 6, 7 of the group 3 can be reached lower opening end face.

Group 3 are volumetric rotary expanders (expanders), in which the expansion process of the combustible mixture performs work on the shaft 4 of the internal combustion engine. If the combustible mixture is complete, it will exit from the upper end of group 3 (shown by the arrow). When the shaft 4 turns, the cooperating elements 5, 6, 7, 15, 16 and 17 in group 1 are defined by the synchronization device 11 in the group 1. Two independent counter-rotating movements of the elements 5, 7, 15, 17 Freedom to move their mating contacts to confine and move group 1 as suction (6 chambers between elements 5,6 and 15,16 along axis Z and between elements 6,7 and 16,17 5 chambers) of the working medium.

As shaft 4 turns, mating elements 8 and 9 in group 2 move their mating contacts along the Z-axis by moving their mating contacts within one independent degree of freedom of rotational movement of element 9 defined by the crank of shaft 4 in group 2. Confine and move the three working chambers that are Group 2 of the combustion section.

When the shaft 4 turns, the mating elements 5', 6', 7', 15', 16', 17' of the group 3 pass through an independent degree of freedom of rotational movement of the elements 6', 16' of the group 3 Move their mating contacts to constrain and move along the Z-axis the working chambers of group 3 (6 chambers and 5 chambers between elements 6', 7', 16', 17'). One complete cycle of the axial movement of the working chamber between the elements 5', 6', 7', 15', 16', 17' during one revolution of the shaft 4 in group 1 during the rotation of the shaft 4 appears 4 times. 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

The associated rotational motion about the main axis Z of the screw machine and about their own axis occurs in all groups 1 to 3 and has three mechanical rotational degrees of freedom.

In the internal combustion engine shown in Figure 1a, elements 5, 15 as mechanically connected rotors and elements 7 and 17 as mechanically connected counter-rotors are simultaneously around the Z axis at the same relative speed ω _{(5, 15} ) = -1 and ω _{(7, 17)} = 1 rotates in the opposite direction. The relative angular velocity of the straight line formed by the center O ₆ -OO ₁₆ of the element 6 as the rotor around the Z axis with respect to the speed of the elements 5, 7 as the rotor is given by ω _re =5, where the element 6 as the rotor-satellite The relative angular velocity ω _s(6,16) of , 16 about their axes O ₆ , O ₁₆ is given by ω _s(6,16) = 0.2.

The compression ratio _k1 in group 1 is determined by the total volume of the six chambers between elements 5, 6 and the total volume of the five chambers between elements 6, 7 during multiple volume change cycles during one revolution of the shaft 4 The sum of the volumes and the total volume of the six chambers between the elements 15, 16 and the ratio of the total volume of the five chambers between the elements 16, 17 are determined, that is:

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

The compression ratio _k2 in group 2 is determined by the ratio of the sum of two total volumes to one total volume during one revolution of the shaft 4, i.e. the first of the six chambers between elements 15 and 16 in group 1 The ratio of the total volume and the second total volume of the five chambers between elements 16 and 17 in group 1 to the total volume of the three combustion chambers in group 2 between elements 8 and 9, that is:

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

The overall degree of compression k of the internal combustion engine is the product of the degrees of compression in groups 1 and 2:

k=k ₁ k ₂ =8(V ₁₀₀ +V ₂₀₀ )/V ₁₄₀

By choosing suitable geometrical volume ratios for the chambers in banks 1 and 2, any compression ratio can be obtained in chamber 140 for the purposes of the present invention as required by different internal combustion engines. Any compression pattern, adiabatic or variable compression pattern is also available. The implementation of chambers 140 of two torsion cycles of elements 8 and 9 makes it possible to carry out the combustion of the fuel/air mixture while the gas is transported axially from one chamber to the other in a constant volume manner. Thereby, the thermodynamic efficiency of the internal combustion engine can be improved.

The exhaust group 3 works with fixed elements 7', 17'. All mating elements 5', 6', 7', 15', 16', 17' together delimit the working chamber of the exhaust section of the rotary machine and move the studio.

Group 3 mechanisms are reversible.

The degree of expansion of the working substances in group 3 is given by the geometrical parameters and the expansion order of the cooperating elements. For the purposes of the present invention, it can be chosen in such a way that the working substance is fully expanded to reduce its pressure to atmospheric pressure. Therefore, no 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, especially when driving vehicles with moment weakening features, only a part of the mechanical energy is used in group 3 and the remainder in an additional volumetric expander 33 (expander, similar to expander 3) Mechanical energy is very advantageous, said expander 33 is shown in dotted lines in Figure 1a. The shaft 34 of the expander 33 (also shown in dotted lines in FIG. 1 a ) is not mechanically connected to the shaft 4 . The rotational mechanical energy is output from the output shaft 34 of the additional expander 33 according to the scheme of a two-shaft internal combustion engine.

In another alternative method, it is also possible to directly inject the combustion products from the outlet of group 3 according to the scheme of an air-injected internal combustion engine in which the compressors of groups 1 and 2 are formed using the method according to the invention Formed, and using the method according to the invention, the expander is formed from group 3 of volumetric rotary screw machines, where fuel combustion can take place at constant volume in the chamber 140 of group 2, so that the thrust of the internal combustion engine can be increased. Fuel combustion may also take place in an outer combustion chamber (not shown) connected to combustion chamber 140 .

Moreover, in order to be able to utilize not only the mechanical energy of the working substance but also (completely) thermal energy, hot gas discharges can be provided in special heat exchangers (not shown in Fig. The air passing through groups 1 to 2 is heated, which increases its pressure. Therefore, in the present invention, the thermal and mechanical energy of the working substance can be fully utilized in the internal combustion engine, so that its efficiency can be increased, and at the same time it can work silently at the pressure and temperature of the exhaust gas at atmospheric levels.

The inversion of shaft 4 and element 5 formed by synchronizing device 11 in group 1 allows the connection of said internal combustion engine with reversing mechanisms such as air propellers or water impellers, lawnmowers, saws, reversing cutting elements of crushers, etc. . It can also realize the connection with the reverse turbine or main rotor of the aircraft.

When a positive displacement screw machine is used, the method may synchronize or simultaneously transform the motion of the mating elements during transport of the working substance through the differential motion mechanism in group 1 .

Claims (7)

1. One kind be used in rotating screw machine (energy transformation method of Fig. 1 in a), described screw conveyer comprises:

   First group of male and female mating member (5,6,7; 15,16,17); And

   At least the second group male and female mating member (8,9; 5 ', 6 ', 7 '; 15 ', 16 ', 17 '), their layouts of being separated by along the central axis of described screw conveyer and described first group (1),

   Wherein, the female element (5,6,15,16 in every group; 8; 5 ', 6 ', 15 ', 16 ') having respectively with first longitudinal axis (Z) is the interior contoured surface (105,106,115,116 at center; 108; 105 ', 106 ', 115 ', 116 ') and

   Male element (6,7,16,17 in every group (1,2,3); 9; 6 ', 7 ', 16 ', 17 ') having respectively with second longitudinal axis is the outer surface (206,207,216,217 at center; 209; 206 ', 207 ', 216 ', 217 '),

   Described first and second longitudinal axis are parallel to each other,

   Described male element is placed in the inner chamber of corresponding female element,

   Wherein, when described public affairs and/or female element rotatablely moved, the working room that is formed between described mother and the male element carried out axial motion, and

   The synchronizing in the following manner that rotatablely moves of different group (1,2,3), promptly the oscillation angle cycle of the axial motion by making described working room has different values and realizes synchronous simultaneous movements between the element in the different group (1,2,3).
2. 2. the method for claim 1 is characterized in that, the described angle cycle reduces from one group to next group, thereby working medium is compressed.
3. 3. the method for claim 1 is characterized in that, the described angle cycle increases from one group to next group, thereby working medium is expanded.
4. 4. as arbitrary described method in the claim of front, the axle (4) that uses hollow and wherein the working medium of flowing through realize making the synchronizing that rotatablely moves between the different group (1,2,3).
5. 5. as arbitrary described method in the claim of front, it is characterized in that,

   First group (1) forms differential motion mechanism, and it has three mechanical rotation degrees of freedom, and wherein two degrees of freedom are independently, and

   Second group (2) form planetary body, and it has two mechanical rotation degrees of freedom, and one of them degrees of freedom is independently.
6. 6. as arbitrary described method in the claim of front, it is characterized in that described working medium is extracted and heat supply in heat exchanger.
7. 7. as arbitrary described method in the claim of front, it is characterized in that the mechanical energy in resulting from one of described group is used to drive another device.

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