RU2373400C2 - Double-auger unit of movable working chambers of mechanical compression or using pressure of liquid and/or gaseous working body, method of producing spherical helical wall of spherical auger of double-auger unit - Google Patents

Abstract

FIELD: engines and pumps.

SUBSTANCE: invention relates to compressors or engines. Double-auger unit of movable working chambers of mechanical compression or using pressure of liquid and/or gaseous working body comprises one auger integrating one lengthwise end face of helical wall with bottom, and another auger integrating opposite end face of the like helical wall with bottom. Movable augers are driven by clamping device and/or converting drive. Augers feature spherical or flat shape. Helical walls together with bottoms of both augers are displaced through half the pitch of generating spiral minus sum of thickness of both helical walls. Space between bottoms of both augers is separated by helical walls into tight chambers arranged on both sides of either helical wall. Helical wall of one auger can roll in whatever direction and slide along two helical surfaces of helical wall of the other auger to vary volume of chambers formed and disappeared in space between bottoms of augers.

EFFECT: reduced friction of working surfaces.

24 cl, 34 dwg

Description

Mutually auger block of movable working chambers of mechanical compression or using the pressure of a compressed liquid and / or gaseous working fluid, a method for manufacturing a spherical spiral wall of a spherical screw relates to a device and a method for manufacturing its particular embodiment in the field of engine building.

The scope of the reciprocating auger unit, in combination with the clamping and / or converting drive that ensures its operation, is within the scope of application of piston, rotary piston, vane (vane), screw, gear motors, compressors, pumps, including centrifugal pumps and internal combustion engines, and limited by the efficiency of gas turbine engines

The concept of a reciprocating auger block of movable working chambers of mechanical compression or using the pressure of a compressed liquid and / or gaseous working fluid, consisting in changing the working volumes along the arcs of two spiral coils changing their relative position, can be considered practically identical to the concept of the Sedunov I.P. rotary-wave engine . (RU, patent 2155272 C1, publication 2000.08.27), comprising a rotor installed in a housing including an inlet and an outlet window, a compressor and expansion compartments and a combustion chamber and characterized in that the inner surface of the housing is made in the form of facing vertices facing and lying on one axis of a pair of screw cones like the surface of a rotor mounted at an angle to the axis of the housing, and at least two support nodes, with any point on the helix of the rotor, except for the center, in which the frequency and amplitude of the oscillations is zero made with the ability to make equal angular oscillations relative to the axial line of the housing, and in General, it is possible to rotate the rotor with simultaneous planetary rolling around the inner envelope of the housing. The wave engine has solved the problem of ensuring the positive properties of gas turbine engines and reciprocating machines in one power unit.

The complexity of the implementation of the wave engine is the weak certainty of the geometry of the spiral winding of the rotor and the housing and, accordingly, the complexity of their mathematical description, as well as the lack of manufacturing technology for these parts. The main disadvantage of this design should be considered the impossibility of achieving uniform extremely small gaps between the rotor and the stator, which in itself casts doubt on the operability of the rotor-wave engine at the stated level of technology. All this is a consequence of the spatial trajectory of any point on the working surface of the rotor, which runs sequentially through a smaller, equal and greater distance of the points of the screw housing from the axis of the housing, as well as from the intersection of the axes of the rotor and the housing.

The objective of the invention is a comprehensive differentiation of functional dependencies with the determination of the optimal geometric shape created by the spiral formed chamber-forming complex of parts that:

a) in the working position with the working movement they will give compression comparable to the compression of the chamber-forming piston and on one side of the plugged cylinder of the piston mechanisms;

b) on the part of the working chambers, they have working surfaces with the possibility of reducing or completely eliminating friction, as a result of wear;

c) have the ability to manufacture them.

The achievement of the technical result indicated in the reciprocating screw block of the movable working chambers of mechanical compression or the use of the pressure of a compressed liquid and / or gaseous working fluid is due to the content in this block of the rotor, similar in characteristics to the analog of internal screw winding, and external rotor screw winding, which in fact are extensive screws. The concept of screw winding in this case is applicable with great difficulty, therefore, using a different, more detailed formulation, we can say that the auger block includes one large auger, combining one longitudinal end of the spiral wall with the bottom, and another large auger, combining the opposite longitudinal end face of a similar spiral wall with a bottom. Also, the screws lose the conceptual meaning of the rotor due to the lack of rotation of one screw relative to another in the working movement. Also, the screws lose the conceptual meaning of the housing due to the variety of designs of the clamping devices and / or converting drives, ensuring the working position of the extensive screws with the possibility of working movement, which in different versions allow you to move either one of the screws and both screws at the same time. The choice of a screw, the bottom of which should have a through hole along the axis of the direction of formation of its spiral wall and a radius of not more than the distance from this axis to the nearest point of this spiral wall, will be determined by the specific design of the marked devices that ensure the operation of the reciprocal screw block.

The specified technical result is achieved due to a significantly changed geometric shape of the screws. So, the screws have a spherical or flat shape. The width of the spiral groove of one screw is greater than the thickness of the spiral wall of the other screw. The spiral walls and spiral troughs of both screws have identical forming spirals. The second-order generator of the spiral surface of the spiral wall of one screw is identical to the second-order generator of the spiral wall of the spiral groove of the other screw. The free longitudinal ends of the spiral wall of one screw have the shape of the bottom surface of the trough of another screw. The spiral walls of both screws have a uniform constant height. The spiral walls of both screws have at least one full turn.

It should be noted that with an increase in the number of turns of the spiral walls of the screws, the pressure difference between the working fluid in the emerging working chamber and the working fluid in the ending working chamber increases.

The specified technical result is achieved due to the changed relative working position of the screws. So, the spiral wall of one screw is located in the spiral groove of the other screw. The spiral wall of one screw is rotated along the axis of formation of the spiral wall relative to the spiral wall of the other screw by one hundred eighty degrees. The spiral walls together with their bottoms of both screws are deflected by a half step of the generatrix of the spiral minus the sum of the thicknesses of both spiral walls, which allows the spiral walls in the places of their convergence and divergence to have constantly changing slipping points and constantly changing wedging points. As a result, the space between the bottoms of both screws is divided by spiral walls into sealed chambers, the chambers being located on both sides of any spiral wall.

It must be clarified that the screws, having a spherical form of execution, have an axial relative displacement by deviation, and having a flat form of execution, have a radial relative displacement by deviation.

The indicated technical result is a consequence of a significant change in the nature of the relative working movement of these screws, which is based on the ability of the spiral wall of one screw in any direction to simultaneously roll with its two spiral surfaces along the two spiral surfaces of the spiral wall of the other screw, in which there is a displacement along the spiral arc and simultaneous change in the volume of arising, formed and ceasing in the space between the bottoms of the chambers. In another statement, the working movement is represented as an oscillation of the spiral wall of one screw in the spiral groove of another screw with a spatially closed path of any point. In this case, the working movement of the entire screw and, in particular, the round limit contour of its bottom against the background of the round limit contour of the bottom of the other screw is characterized as oscillation along an arc of a circle.

In the particular case of the use of a reciprocal screw unit, the relative working position of the screws, with the possibility of relative oscillation of the screws along an arc of a circle, is fixed by the offset principal surfaces of the rotatable converting carriage through the repeated surfaces of the round limit circuits on the ring disks combined with the jumpers with jumpers. Moreover, the annular disks are at the limit or moved beyond the dimensions of the reciprocal screw unit of the movable working chambers, and the repeated surface of the circular limit circuit of one screw is mounted on the path of movement of the repeated surface of the circular limit circuit of the other screw. Moreover, with a spherical form of execution of the screws, the repeated surfaces of the limiting round contours of the screws on the ring disks and the principal surfaces of the rotatable converting carriage will be axially displaced planes. Moreover, with a flat form of execution of the screws, the repeated surfaces of the limiting round contours of the screws on the ring disks and the principal surfaces of the rotated converting carriage will be radially displaced cylinders. Moreover, with a flat form of execution of the screws for the purpose of unloading or complete replacement of slipping and wedging points, two conversion drives can be used. Moreover, with a flat form of execution of the screws, it is possible to use a crankshaft or crankshafts as a special case of a converting carriage. In all these cases, it may be useful to install rolling bearings between the repeated surfaces of the limiting circular contours and the principal surfaces of the rotatable conversion carriage.

In another particular case of using a reciprocal screw unit, the relative working position of the screws with the possibility of relative oscillation of the screws along an arc of a circle is fixed in a common housing with the possibility of simultaneous rotation, with each screw rotating relative to its own axis of formation direction. In this case, for the purpose of unloading or completely replacing the slipping and wedging points, the screws are connected to each other by a block of gears with a final gear ratio equal to one.

In cases where cooling, lubrication or supply of the working fluid from the moving auger side may be required, the main reciprocating auger block is supplemented by an additional reciprocating auger block, both reciprocating auger blocks must have a single converting drive, and the flow of lubricating or cooling fluid or working fluid with an additional reciprocal screw unit, it should be carried out from the side of its movable screw through channels located on the kinematic connection of both movable screws to a special the cavity that the bottom of the movable auger of the reciprocal auger block must have. It is possible to use the free side of the bottom of the movable auger of the main reciprocal auger block as the bottom of the movable screw of the additional reciprocal screw unit, which will greatly simplify the design. It should be noted that with a spherical form of execution, the additional and main reciprocal screw blocks must be located so that the spherical bottoms have a single center of spheres.

The specified technical result is a consequence of the operation of the reciprocating screw unit. So, a liquid or gaseous working fluid, as compressed as possible in the region of the passage opening, the compression ratio of which decreases as the working chambers move to the periphery from the axis of the direction of formation of the spiral walls and has the smallest compression of the open chamber in the region of the limiting bottom contour, presses, creating a liquid or gaseous pad on the bottom surface of the screws. This decreases, with the possibility of complete cessation, both the pressure and the friction force of the spiral wall of one screw on the bottom of the other screw. The noted pressure and friction force are inversely proportional to the pressure of the working fluid and are directly proportional to the gravity of the screw and the gravity of the moving parts of the pressing device and / or converting drive.

In the particular case of the use of a reciprocal screw unit in order to balance the pressure of the working fluid on the bottom of one screw and to ensure that the spiral wall of one screw is located in the spiral groove of the other screw, the screw can have two similar spiral walls, one on each side of the bottom of this screw. Moreover, each spiral wall of this auger is provided with a similar spiral groove of the other two augers, which are connected to each other through their bottoms by jumpers, and an additional through hole in the bottom, depending on the purpose and the whole structure of which they are part, can be provided as any two augers , and all three augers. In another particular case, with a flat form of execution of the reciprocating screw unit, the pressure of the working fluid on the screw bottoms is compensated by the pressure of the pressure plate of the pressure device, connected by jumpers of the pressure device with one screw, directly onto the free side of the bottom of the other screw, or by jumpers combined with another screw, or ring disks combined with another auger. In this case, it may be useful to install the pressure bearings between the pressure disk and the pressure elements combined with the bottom of the other auger. It may also be advisable to make it possible to adjust the tightness of the working chambers and reduce or eliminate the frictional force on the bottom surfaces of the jumper of the pressure device to be able to adjust the distance from the pressure disk of the pressure device to the screw with which it is fixedly connected.

Due to the achievement of this result, it becomes possible to use a reciprocating auger unit as the basis of the engine part in an internal combustion engine, in which solid or combined fuel can be used along with gaseous or liquid fuel. For this, the auger block is reciprocal, along with two augers, in its design includes a combustion chamber, the operation of which is provided by gaseous, or liquid, or solid, or combined fuel supply devices, a compressor and a compressed air supply channel, and an ignition system. The housing of the combustion chamber is combined with the bottom from the passage opening with the possibility of supplying combustion products to the movable working chambers, or the combustion chamber itself is arranged in the reciprocal screw unit, taking into account the mobility of the spiral walls. In this case, it becomes possible to organize a partially closed thermodynamic cycle. In order to reduce the temperature expansion of the material of the reciprocal screw unit, to reduce temperature losses and increase the efficiency in the internal combustion engine, the spiral walls and / or the bottoms of the screws and / or the combustion chamber are provided with heat exchange channels, as well as holes or nozzles for supplying a heated working fluid of circular thermodynamic cycle in movable working chambers. And on the basis of creating a closed circular thermodynamic cycle, it is possible to create a sufficiently effective heat engine.

The objective of the method is the manufacture of a spherical spiral wall of a spherical screw of a reciprocating screw block of movable working chambers of mechanical compression or using the pressure of a compressed liquid and / or gaseous working fluid.

The specified technical result of a method for manufacturing a spherical spiral wall of a spherical screw is achieved by cutting a rotating spherical billet with a spherical wall thickness of not less than the height of the spiral wall. Moreover, the cutting edge of the cutting tool is simultaneously rotated around the center of the spherical workpiece, and the axis of rotation of the cutting edge of the cutting tool is perpendicular to the axis of rotation of the spherical workpiece. The trajectory of the cutting edge of the cutting tool in the body of the spherical workpiece is a first-order generatrix of the spiral wall and spiral groove described by a system of three trigonometric equalities.

In order to reduce stress concentrations arising during the application of the spiral wall, the second-order generator of the spiral wall and spiral groove is changed by changing the shape of the arc of the cutting edge of the cutting tool.

The content of the graphic part.

Group 1 - spiral walls. Axonometric view.

Subgroup 1.1 - spherical spiral walls.

Figure 1 - spherical spiral wall.

Figure 2 - diametrically opposite position of the two spherical spiral walls of figure 1.

Figure 3, figure 4, figure 5, figure 6 is a deviation from the diametrically opposite position of the spherical spiral walls of figure 2 in four different directions. These figures in combination characterize the creeping rolling of spherical spiral walls.

Subgroup 1.2 - flat spiral walls.

7 - spiral walls in the plane. Identity of flat spiral walls. Axonometric view.

Fig - diametrically opposite position of the flat spiral walls of figure 7. Top view.

Fig. 8, Fig. 9, Fig. 11, Fig. 12 is a deviation from the diametrically opposite position of the spherical spiral walls of Fig. 7 in four different directions. These figures in combination characterize the creeping rolling of flat spiral walls.

Group 2 - a conceptual model of the device and kinematic relationships of a reciprocating screw block of movable working chambers of mechanical compression or using the pressure of a compressed liquid and / or gaseous working fluid and a converting drive with a fixed and movable augers.

Subgroup 2.1 - a conceptual model of the design and kinematic connections of a spherical reciprocal screw block of movable working chambers with a single flow direction and a different duty cycle length. In this subgroup, the spiral walls correspond to the truncated spiral walls of subgroup 1.1. The required dissection of the stator into two components for the possibility of assembly of the screws is not shown in accordance with the general task. 13 is a main view. Fig. 14 is a view A from Fig. 13. Fig. 15 is a view B of Fig. 13. Fig.16 is a section In with Fig.13. Fig - sectional view of a stationary spherical screw with jumpers and an annular disk of this subgroup. Fig - movable spherical auger with jumpers and an annular disk of this subgroup.

Subgroup 2.2 - a conceptual model of the design and kinematic relationships of a flat reciprocating auger block of movable working chambers with a uniform flow direction and an equal working cycle length, with a clamping device, with a converting drive and with a fixed and movable augers. In this subgroup, the spiral walls correspond to the spiral walls of subgroup 1.2. Fig. 20 is a main view. Fig. 19 is a view A from Fig. 20. Figure 21 is a section B from Figure 20. Figure 22 is a section B from Figure 19. Fig is a perspective view of a movable flat screw with jumpers and an annular disk of this subgroup. 24 is a perspective view of a movable flat screw with a jumper and an annular disk of this subgroup.

In group 2 it is noted:

Detail position 1 - fixed auger and its elements:

- position 1.1 - the bottom of the fixed screw and its surface:

- position 1.1.1 - bottom surface,

- position 1.1.2 - round limit circuit,

- position 1.2 - the spiral wall of the fixed screw and its surface:

- position 1.2.1 - outer spiral surface,

- position 1.2.2 - inner spiral surface,

- position 1.2.3 - longitudinal end surface,

- position 1.3 - jumper,

- position 1.4 - the annular disk and its surface:

- position 1.4.1 is the repeated surface of the round limit contour,

- position 1.5 - arc of the equation of the length of the duty cycle and flow direction,

Detail position 2 - movable auger and its elements:

- position 2.1 - the bottom of the moving auger and its surface:

- position 2.1.1 - bottom surface,

- position 2.1.2 - round limit circuit,

- position 2.2 - the spiral wall of the moving screw and its surface:

- position 2.2.1 - outer spiral surface,

- position 2.2.2 - inner spiral surface,

- position 2.2.3 - longitudinal end surface,

- position 2.3 - jumper,

- position 2.4 - the annular disk and its surface:

- position 2.4.1 is the repeated surface of the round limit contour.

Detail position 3 - transforming carriage.

Detail item 4 - bearing.

Detail item 5 - output shaft.

Detail item 6 - centralizer of the output shaft (unprincipled).

A device that compensates for the breaking strength of a working body with an adjustment mechanism:

Detail item 7 - bolt.

Detail item 8 - nut.

Detail item 9 - pressure plate.

Detail item 10 - hold-down bearing.

Instant characteristics of working volumes:

- position 11 - moment camera,

- position 11.1 - variable (moment) wedging point,

- position 11.2 - detachable cameras,

- position 11.3 - shared cameras,

- position 11.4 - the points of convergence of the spiral walls and at the same time the variable (moment) wedging points of the shared compartments.

Group 3 includes FIG. 25 and FIG. 26 and are drawings characterizing the working movement of the reciprocating screw unit by means of the trajectory of the points of one spherical screw relative to another spherical screw. The amplitude of the oscillation, i.e. the width of the proposed spiral groove is taken arbitrarily. For convenience, the trajectories are shown at different (different from axonometric) viewing angles. The trajectory itself is represented by sixteen point positions, which are obtained as a result of sixteen consecutive positions of the movable spherical screw relative to the stationary spherical screw, taking place in one complete cycle of the working movement. In order to characterize the changes in the trim of the movable spherical screw, the points are shown as the center of the coordinate system. On Fig depicted a segment of the bottom of the movable spherical screw pos.2 with the trajectory of the point coinciding with the axis of the hemisphere (the axis of the direction of formation of the arc of the spherical spiral of the alleged spiral wall of this screw), the segment of the bottom of the fixed spherical screw pos.1 and its axis. For convenience, the screw through passage is excluded from the figure. On Fig shows the trajectory of the point of the moving screw against the background of the segment of the fixed screw of Fig.25, as well as the trajectory of the second point located on the bottom of the moving screw, the segment of which is shown in Fig.25, but remote from the axis of the hemisphere at an angle of forty-five degrees, and the trajectory of the third point of the same bottom of the moving screw but remote from the axis of the hemisphere by an angle of ninety degrees in a plane perpendicular to the plane formed by the center of the spheres of the first and second points. The figure highlighted by indicating the points of the bottom of the screw in one relative position of the bottoms shown in figure 25.

Group 4 - Examples.

Subgroup 4.1 - An example of a reciprocating auger block of movable working chambers of mechanical compression or using the pressure of a compressed liquid and / or gaseous working fluid in an internal combustion engine. Fig - section of the engine, the main view. Fig. 28 is a section A of the motor part of the engine of Fig. 27. Fig.29 is a sectional view of the compressor part of the engine of Fig.27.

In subgroup 4.1 it is noted:

Functional parts: K1 and K2 - compressors, D1 and D2 - motor (traction parts).

Position 1 - fixed screw combined with jumpers and disks into a single housing, position 1.2 - spiral wall of the fixed screw, position 2 - movable screw of engines and compressors, position 2.1 - bottom of the moving screw, position 2.2 - spiral wall of the moving screw, position 2.3 - movable auger jumper, position 2.4 - movable auger disk, position 4 - bearing, position 5 - crankshaft, position 12 - oil inlet channel, which is a movable oil pipe, position 13 - supporting cylinder, position 14 - discharge oil channel, position 15 - channelair pumping, position 16 - the start channel, position 17 - the check valve, position 18 - the fuel injection nozzle, position 19 - the constant heating coil, position 20 - the exhaust pipe, position 21 - the air pipe.

Subgroup 4.2 - axial, reciprocating rotary screw type oil pump - Fig.30.

In subgroup 4.2 it is noted:

position 1 '- driven auger, position 1'.1 - the bottom of the driven screw, position 1'.2 - the spiral wall of the spiral driven auger, position 1'.5 - ring guides, position 1.6 - a bevel gear with a disk and jumpers of the driven screw, position 1.7 - pins of the spiral driven screw, position 2 - leading screw, position 2.2 - spiral wall of the leading screw, position 2.6 - bevel gear of the driving screw, position 2.7 - pins of the driving screw, position 5 - drive shaft, position 22 - housing, position 23 - seal, position 24 - oil supply pipe, position 25 - exhaust tubes.

Subgroup 4.3 is a diagram of an internal combustion engine (ICE) with a partially closed thermodynamic cycle and combined fuel with a combustion chamber of a reciprocating auger block of its engine part.

On Fig - in a series of general organization of the internal combustion engine with a partially closed thermodynamic cycle and combined fuel in more detail shows the combustion chamber of the reciprocating screw unit of the engine part.

In subgroup 4.3 it is noted:

position 19 - constant glow coil, position 26 - combustion chamber body, position 27 - solid fuel, position 28 - solid fuel supply piston, position 29 - heat exchanger.

Group 5 - a schematic diagram of a set of technical conditions, which should be provided with tools and equipment in the manufacture of a spherical screw. As an example, the spiral wall of subgroup 2.1 is used.

Fig - manufacturing one screw. Fig - manufacturing another screw. Fig. 34 is a cutting edge of a cutting tool, i.e. the cutting edge is shown as forming a second order for the milling cutters of Fig. 32. and Fig. 33.

In group 5 it is noted:

position 30 is the plane and direction of rotation of the spherical workpiece, position 31 is the axis of rotation of the spherical workpiece, position 32 is the plane and direction of rotation of the cutter, position 33 is the axis of rotation of the cutter relative to the sphere, (this means the simultaneous rotation of the cutter around its own axis of formation of the body of revolution) , position 34 is the milling cutter, position 35 is the trajectory of the cutting edge of the milling cutter in the body of the spherical workpiece (the path is formed only at a certain ratio of the speed of rotation of the spherical workpiece and the speed of rotation of the fr races).

The principles of shaping and the principle of operation of a reciprocating auger block of movable working chambers of mechanical compression or the use of pressure of a compressed liquid and / or gaseous working fluid and converting drives.

There are two options under which it is possible to create the necessary conditions both for equal clearances and for the necessary tightness of the working chambers of the screws. Both variants are classified according to their common geometry into 1) spherical and 2) flat.

In this section, along with the geometry of groups 1 and 2 of the graphic part, the organization of the kinematic dependences of the reciprocating auger block of movable working chambers of mechanical compression or the use of pressure of a compressed liquid and / or gaseous working fluid is considered.

The shape of a spherical spiral wall.

An arc of a spherical spiral is formed on the surface of a sphere from its center, in the direction of any axis of the sphere. In our case, in the direction of the forming axis of the truncated sphere. The spiral pitch in this case is more convenient to set with angular values.

The spherical spiral wall of FIG. 1 is formed between two spheres with one common center. Its cross section is a figure with four sides. The two end sides of the cross-section (surface pos.1.2.3 of Fig.17 and pos.2.2.3 of Fig.18) repeat the parts of the corresponding arcs of circles (sections of the corresponding spheres) and are defined as longitudinal end surfaces at the volute spiral wall. The other two sides are segments lying on conditional lines that pass through the common center of the forming spheres. These surfaces of the spiral walls located between the end surfaces will be represented as spiral surfaces. In this case, the surface closest to the single pole will be represented as the internal pos.1.2.2 and 2.2.2, and the distant, relative to the same pole, as the outer pos.1.2.1 and 2.2.1 of Figs. 17 and 18. It should be noted that the length of the arc and the height of the working surfaces of the spiral wall are equal as conditional surfaces, offset by rotation relative to the generatrix of the spheres by an angle that provides the required thickness of the spiral wall.

The positions of the spherical spiral walls.

The principle of operation of the mutually auger block of movable working chambers of mechanical compression or the use of pressure of a compressed liquid and / or gaseous working fluid is enclosed in two spherical spiral walls with exactly the same generatrix spiral, offset from each other by a hundred and eighty degrees rotation relative to the generatrix of the truncated spheres (Fig. 2). One of them is considered as not changing its position with respect to any point that does not belong to the system. Another deviates in any direction until full contact of all the corresponding points of the spiral surfaces of the spiral walls (figure 3). The matching corresponding points in the assembly of the spiral walls are variable points that are simultaneously characterized as supporting, wedged and slipping. Contact points between the teeth of the driving and driven gears of a gear possess similar wedging and slipping characteristics.

Considering such a position of the spherical spiral walls in statics, one can say that one spiral wall was formed between the surfaces of the truncated spheres of the other spiral wall, in a diametrically opposite position, with its own axis of the spiral formation direction deviated from the axis of the formation of the spheres by an angle equal to half the spherical pitch angle spirals minus the sum of the angles of thickness of these spiral walls. Here, we note that the cross sections of the spiral walls can vary within the limits of the identity of the surfaces being joined, while the first generatrix of the spiral remains unchanged. The spiral wall in the current presentation is defined as the base, and the whole range of options as similar.

With a sequential change in the direction of deviation of the conventional axes of spiral formation, i.e. when the direction of deviation changes, the spiral wall changes its position (Figs. 3, 4, 5, 6), it will oscillate within the trench without changing its position of the spiral wall. Since the ratio of the contact length of the outer spiral surface of one spiral wall to the contact length of the inner spiral surface of the other spiral wall is inversely proportional to the ratio of the length of the contact inner and outer spiral surfaces of these spiral walls, the friction forces arising from the successive change of variable reference points will be equal. In fact, one spiral wall will roll with slipping simultaneously by two spiral surfaces along two spiral surfaces of the other spiral wall, while rotation of one spiral wall relative to the other will not occur.

Truncated from a hemisphere to an infinitely small part of the sphere.

Setting the spherical spiral walls to the working position involves screwing one spiral wall into another like cylindrical ones. However, the screwing of spherical spiral walls is possible only with a number of parametric restrictions in the conditions of formation of these spiral walls. For example, it is obvious that at least one spiral should be truncated to at least a hemisphere. Also the role is played by the ratio of the radii of the forming spheres, the pitch, the number of turns, the starting point of the spherical spiral. The assembly of the spherical spiral walls shown in subgroups 2.1 and 1.1 of the graphic part cannot be assembled by screwing. In fact, both spiral walls must be dissected into its component parts. With a composite spiral wall of a full sphere in a practical assembly, a spiral wall with one full turn is possible in order to achieve the greatest step. Perhaps in the practical assembly of the composite spiral wall of a complete sphere with several turns. This may be interesting in thermodynamic processes.

Such practical assemblies lead to a significant complication of the design. Theoretically, this is possible, but almost unlikely to be appropriate. Therefore, assemblies of spherical spiral walls will be considered only as truncated from half the sphere. It is easier in practical spherical spiral walls, both for assembly and for manufacturing, to increase the radii of the spheres, to reduce the step in angular quantities (the linear step can be preserved) and to truncate the sphere to its infinitesimal part.

Flat spiral wall.

The archimedean spiral forming a flat spiral wall is an arc of a spiral on a plane.

Flat spiral walls are close to a spherical spiral wall with an infinitely large radius of the forming spheres and other, relatively small, parameters. They have absolutely identical inherent properties and properties in the assembly. In the subgroup 1.2 of the graphic part, their identity is shown (Fig. 7), displacement by a turn of one hundred and eighty degrees (Fig. 8), deviations of the forming points to the coincidence of the variable support, slipping, wedging points and the sliding rolling of the spiral walls (relative vibrations) (Fig. 7). 9, 10, 11, 12). The section of the base flat spiral wall will be a rectangle. The axis of the direction of formation is a straight line, perpendicular to the plane of the generatrix of the spiral and passing through the point of formation of this generatrix of the spiral (in relation to the circle, the point of formation is the center).

Augers. Formation of sealed working chambers.

Working closed chambers are formed between two assembled spiral walls pos.1.2 and 2.2 and two bottoms pos.1.1 and 2.1 from the side of the longitudinal end surfaces of the spiral walls having the shape of the general geometry of these spirals (Fig.17, 18, 23 and 24) (in spherical chambers are two truncated spheres, and in flat ones - two flat disks). One of the bottoms has a through hole along the axis of the direction of formation of its spiral wall. For the best tightness and kinematic connection, the bottoms and spiral walls are tied in pairs into a single screw corresponding to each pair. One of the screws is defined as stationary, not changing its spatial position, and the other as mobile. The reciprocal screw block thus obtained in the assembly space will have one arising, one formed and one discontinuing or two arising and two interrupting chambers with one turn of the spiral wall, and with more turns, more chambers isolated from each other. When the spirals oscillate, these chambers will move along the arc of the spirals. As the cameras move away from the axis of formation, their volumes increase. And vice versa, when changing the direction of oscillation of the moving screw. To demonstrate the direction of oscillations and changes in the inter-helical space should be considered figure 3, 4, 5, 6 and figure 9, 10, 11, 12 in direct and reverse sequence.

The working chamber on the example of pos. 11 of Fig. 22 is characterized not only by its volume, but also by its own arc of the variable reference points of pos. 11.1 along the height of the spiral surface and providing tightness along the arc of the height of the spiral surface by the variable reference points of pos. 11.4 separated by the spiral walls of the movable and fixed augers, adjacent working chambers, item 11.2.

The area of the constantly changing part of the spiral wall from the variable reference points of a particular chamber to the variable reference points of the large adjacent chambers will be larger than the area of the constantly changing part of the spiral wall from the variable reference points of the same chamber to the variable reference points of the smaller adjacent chambers. What makes it possible to use a movable spiral chamber in the mode of using the pressure energy of the working fluid (in engine mode). For rough estimates, this difference will depend on the removal of the variable reference points from the axis of formation and the pitch of the spiral. From this we can conclude that, no matter how much the working volume has changed, the efficiently used working area in physical terms will not change. And all relative performance indicators will decline.

When pressure arises in the working chambers, the block of movable chambers in any mode will have working chambers with relatively high pressure and working chambers with relatively low pressure. A higher pressure will correspond to a relatively smaller volume of the working chamber and vice versa. Thus, the nature of the movement of the moving auger will determine not only the difference of the (constantly changing) shoulders of the sections of the spiral wall of the moving auger relative to the (constantly changing) support points of a certain (constantly changing) working chamber, but also the difference of the (constantly changing) pressure of this working chamber, item 11 and (constantly changing) pressure of chambers pos. 11.3 separated by spiral walls and separated by alternating reference points of adjacent (constantly changing) working chambers of pos. 11.2 of Fig. 22.

Wave motion on the limit circuit. Conversion drive.

The limiting contours of augers means the visible round contour of pos. 2.1.2 of the bottom of the moving auger, closing its space, against the background of a similar visible round contour of pos. 1.1.2 of the bottom of the fixed auger. In the deviated operating position, the limit contour of the fixed screw, for example, reciprocally screw block Fig and Fig, conditionally divide the limit contour of the deviated movable screw into two parts. A portion of the limit contour of the movable screw extending beyond the limit contour of the fixed screw forms a ridge. When the spiral walls oscillate, the crest of the movable screw will move along the circular arc of the circular contour of the fixed screw. Despite the constantly changing composition of the points, the comb as a three-dimensional figure will remain unchanged. The same is true for part of the contour of the movable screw located within the contour of the space of the fixed screw.

The task of the transforming drive is to convert the wave motion along an arc of a circle into rotational motion. The actual conversion drive consists of an annular disk pos. 1.4 of a fixed screw with a repeated surface pos. 1.4.1 of a round limit contour of the bottom of a movable screw, a fixed jumper of pos. 1.3 with a bottom of pos. 1.1 of a fixed screw, an annular disk pos. 2.4 of a movable screw with repeated the surface of pos. 2.4.1 of the round limit contour of the bottom of the movable screw fixedly connected by a jumper of pos. 2.3 with the bottom of pos. 2.1 of the movable screw and the rotating transforming carriage of pos. 3, sandwiched between these repeated surfaces.

The jumpers and the annular disk of the fixed auger are designed to repeat the points of the round limit contour pos.1.4. fixed auger in the directions of movement of the repeated surface pos.2.4.1 of the circular limit contour of the movable auger. The conversion carriage is an independent element. Its principal points are formed on the surfaces of repeated limiting contours at rest, when the spiral walls have a relative working position. Those. The principal surfaces of the converting carriage are in the spherical version axially displaced by planes, and in a variant on the plane by radially displaced cylinders. The remaining, unprincipled points are designed for fixed communication between principal surfaces. In engine mode, the comb as a three-dimensional figure will push the transforming carriage into rotational motion. From the point of view of the entire reciprocal screw unit, the relative repeated limit circuits will squeeze the transforming carriage into rotational motion from the side of the larger shoulder of the spiral of the current working chambers. And from the side of the smaller shoulder of the spiral of the current working chambers, the movable auger will be crushed and together with it the same current working chambers. In fact, the transforming carriage during its operation controls the trajectory of each point of the moving screw and completely replaces the support character of the contact points of the spiral walls.

Between the surfaces of the repeated limit circuits and the principal surfaces, it is advisable to install bearings pos.4, which reduce friction. For this, the principal surfaces of the transforming carriage should be built with the appropriate clearance from the surfaces of the repeated limit circuits or formed on the conditional surfaces of the repeated same limit circuits.

Torque transmission can be arranged both through a rotatable shaft from the center of rotation, pos. 5, and through gears from the periphery of the converting carriage. The center of rotation of the transforming carriage is defined as independent and, as a rule, coincides with one of the points of the axis of formation direction. But, for example, with the flat forms of the screws, both the repeated surfaces of the limiting contours and the center of rotation can be shifted from the axes of the direction of formation of the movable and fixed screw to the periphery of the bottoms. So, a crankshaft can be used as a conversion carriage with a flat reciprocal screw unit.

A converting drive for a reciprocating auger block of movable working chambers can also be arranged on a rotary basis. When the rotary mechanism is designed, both screws in the working position, clamped in a common housing, rotate at a uniform angular speed each around its own axis of formation direction. The casing has a passage opening matching the screw passage in the maximum pressure zone, ensuring the circulation of the high-pressure working fluid with an external source or consumer, depending on the purpose. Another passage opening provides a message of the working fluid in the low pressure zone. The low and high pressure zones of the working fluid of the common housing are separated by a snug fit with the free surface of the bottom having a through hole and the corresponding surface of the housing. In order to reduce the friction area and lubricate the friction surfaces between the housing and the screws, rings can be installed with the possibility of rotation of the screws and hermetically segregating zones of different pressure of the housing. A screw that does not have a through hole is combined with a power take-off shaft with the shaft axis coinciding with the axis of the formation direction of this screw. The power take-off shaft extends beyond the common housing. In order to replace the wedging and slipping characteristics of the points of convergence of the spiral walls, the screws can be connected by a bypass gear block with a final gear ratio equal to one.

In fact, with any variations in the implementation of the working position and the working movement of the reciprocating screw unit, a set of devices is required to ensure such a position and such a movement. Or, in other words, the mutually auger block should be part of a whole mutually auger mechanism.

The trajectory of the point.

The required fit of the free longitudinal ends of the spiral walls to the bottom surface of the bottom in order to achieve the required sealing of the movable working chambers during the working movement of one screw relative to the other screw is characterized by the trajectory of any point of the moving screw. Including the trajectory of any point located on the free longitudinal end of the spiral wall.

In order to characterize the tangent of the tangent plane, the moment spatial position of the point is represented as the center of the Cartesian coordinate system, which itself changes the relative spatial position.

The points of a flat auger oscillate along the intrinsic trajectory of a closed circular arc, characteristic only of this point.

The trajectory of a closed arc of a circle have points located on the axis of the direction of formation of the spherical screw of Fig.25. But the moment spatial position of the point differs from the spatial position of the point of the flat screw and is determined by the center point of the spheres. As the studied point (points I, II, III in Fig. 26) moves away from the axis of the formation direction, its trajectory gradually stretches into a shape similar to a tearing drop, passes into the shape of an asymmetric figure eight, and on the plane perpendicular to the axis of formation direction, the studied point will be have a trajectory of a symmetric figure of eight stretched along a spherical surface.

In other words, during the working movement, the free longitudinal ends of the spiral walls during the working movement of the screws will always be at a set distance from the bottom surface of the bottom.

The difference and the equation of the length of duty cycles and flow directions.

The degree of change in the pressure of the working fluid in the working cycle directly depends on the number of turns of the spiral wall. Or, otherwise, from the number of revolutions made by any elementary part of this working fluid. Mutually auger block has two parallel duty cycles, with a time difference of half a revolution of the working chamber. One working cycle passes between the inner spiral surface of one screw and the outer spiral surface of the other screw. Another working cycle takes place between the outer spiral surface of one screw and the inner spiral surface of the other screw.

Under these conditions, attention should be paid to the flow message (supply or discharge, depending on the operating mode) with the low pressure zone. The spiral walls displaced by one hundred eighty degrees carry the divided flow tangentially from diametrically opposite points. It is possible to specify a single direction, both truncating the spiral wall of one screw to the end of the spiral wall of the other screw, and the arc of the flow direction from the end of the spiral wall of one screw to the end of the spiral wall of the other screw. In the first case, the duty cycle from the side of the outer spiral surface of one screw will be less than the duty cycle from the side of the inner spiral surface of the same spiral wall. Consequently, the effluent flows will merge into one with a certain pressure difference.

The spherical reciprocal screw block of the movable working chambers of the subgroup 2.1 of the graphic part is shown with the difference of the working cycles. A flat reciprocating screw unit of the movable working chambers of subgroup 2.2 of the graphic part with an arc of the direction of flow with equal working cycles.

Pillow of the working fluid. Clamping device.

Mutually auger block of movable working chambers assumes an average pressure of the working fluid exceeding the external (atmospheric) pressure. Under these conditions, the force of the compressed working fluid directed to the bottom surfaces of pos.1.1.1 and pos.2.1.1 of the bottoms of pos.1.1 and pos.2.1 tends to spread the assembly into separate parts and thereby destroy the system of functional connections.

The reciprocal spherical screw unit compensates for these forces with its own device and converter drive. In the flat version, it is necessary to use additional devices that compensate for the breaking forces arising in the working chambers. The meaning of such devices is to enclose one screw through the clamp bearing pos. 10, the clamping disc pos. 9 and the disc pos. 1.4 and jumpers pos. 1.3 of another screw in the space of another screw. In practical devices that compensate for breaking forces, it is advisable to use adjustment mechanisms (bolt pos. 7 and nut pos. 8).

Of particular interest is the adjustment of the position of the screw in the flat mutually auger blocks of the movable working chambers in conditions of a significant temperature difference. With temperature expansions (first of all, metals are assumed) of identical screws, their linear characteristics will equally change, and the removal of the longitudinal end surfaces must be set by adjustment mechanisms. In the presented subgroup 2.2 of the graphic part, the simplest adjustment mechanism is used (in the form of bursting bolts and nuts). With the use of more complex devices, automatic adjustment is possible, including during the operation of the mutually auger block of movable working chambers. With a significant modification of a flat reciprocating auger block of movable working chambers, it is possible to create a flat mutually auger block of movable working chambers with a changing total working volume and using this mechanism as a gearbox.

Features of the reciprocating auger unit when organizing related systems on a moving auger.

Associated systems are understood as possible systems: an equilibrium bottom pressure system, a lubrication system, a cooling system, an injection system, etc. systems that may be required on a screw that changes its position when solving specific problems.

The basis for creating the necessary flows on the main movable screw is a mutually auger block of movable working chambers with the same step forming spirals as the step of forming spirals of the main mutually auger block of movable working chambers. The centers of the spheres of the accompanying and the main reciprocal screw blocks must coincide, and the screws themselves must have a single converting drive. The flat accompanying relatively movable auger should be fixedly connected to the main relatively movable auger, and the accompanying relatively fixed auger should be motionlessly connected to the main relatively fixed auger. The position of the accompanying flat reciprocal auger block with respect to the main flat reciprocal auger block does not matter. It is possible to use the reverse side of the main auger as a companion screw.

The flow of the accompanying system from the accompanying reciprocal screw unit is carried out from the side of its movable screw, along the contours of the kinematic connection of both movable screws to the main movable screw. And when using a reciprocal screw unit in rotor-type mechanisms, the flow is communicated along the axis of rotation along the channels with the simultaneous rotation of their screws. It is this arrangement that provides absolutely reliable connections of related systems on the rototiva.

Features of a reciprocating auger block used as the basis for the motor part of an internal combustion engine.

The specifics of the design of the reciprocating auger block used as the basis for the engine part of the internal combustion engine requires the supply of combustion products obtained as a result of ignition of the combustible mixture of compressed air from the compressor and fuel into the mobile working chambers. To this end, a reciprocating screw unit includes a combustion chamber in its design. Its operation is provided by gaseous, or liquid, or solid, or combined fuel supply devices, as well as a compressor and a compressed air supply channel and an ignition system. The casing of the chamber is combined with the bottom from the side of the passage opening in order to supply combustion products to the movable working chambers. Perhaps the device of the combustion chamber in the reciprocal screw unit, taking into account the mobility of the spiral walls.

Also, the design specificity is due to the presence of high temperatures during the operation of these ICEs, which lead to linear expansion of the screws, more precisely, to the expansion of the material from which they are made (first of all, metals are assumed). So, while expanding the bottoms, the gap between the spiral wall of one screw and the wall of the spiral groove of the other screw should increase, and an increase in the height of the spiral wall will lead to jamming. In order to divert the temperature from the screws, their cavities are provided with channels for the circulation of coolant.

If there are openings connecting the channels for the circulation of the coolant with the movable working chambers, it is possible to organize a closed thermodynamic cycle for this fluid. It is possible to organize the injection of a heated working fluid of a closed thermodynamic cycle into the movable working chambers by means of the corresponding nozzle holes installed in place.

Examples of practical implementation.

Mutual flat auger internal combustion engine.

Mutually auger internal combustion engines consist of two integral mutually auger blocks of movable working chambers of mechanical compression or using the pressure of a compressed gaseous working fluid with a possible different design solution and relative position. One of the blocks performs the function of a compressor, the other - the traction function of the engine.

An example of a planar spiral formed subgroup internal combustion engine. 4.1 of the graphic part is presented as a two-pair engine with an oncoming two-tier arrangement of mutually auger blocks. The motor housing is integral with the bottom, jumpers and ring disks of the fixed screws pos.1. The communication of the working flows between the reciprocal screw blocks occurs through the holes in the center of the bottoms of the movable and fixed screws, and the lubrication system - through the oil inlet pos. 12 through the cylinders pos. 13 of the section oil line through the bearings pos. 4 of the converting drive through the discharge oil channel pos. 14 . The spiral walls of the engines D1 and D2 with respect to the spiral walls of the compressors K1 and K2 have, due to the larger pitch and height in the zone of maximum pressure, a large working area and provide motor (traction) function. The spiral walls of compressors K1 and K2 have a winding opposite to the spiral walls of engines D1 and D2, thus providing a compressor function. All the bottoms of the movable screws pos.2 have two-sided spiral winding and reciprocal spiral grooves, thus balancing the gas pressure on the bottom surfaces of the blocks arising during the operation. The movable screw itself along the axis of the crankshaft is held through its jumpers, pos. 2.3, on its disks, pos. 2.4, sandwiched between the cylinders pos. 13 of the section oil line, motionlessly connected with the ring disks, pos. 1.4 of the fixed auger. The connecting rod journals of two crankshafts, pos. 5, have alternately diametrically opposite positions, forcing the movable augers to move along an arc of a circle with a difference of one hundred and eighty degrees and, in combination with the equality of the weights of the movable augers, completely balance the entire engine. The axis of the crank pin crankshaft is offset relative to the main journals (necks of the fixed screw) by an amount that provides an extremely small clearance between the spiral walls of the movable and fixed screws. The engine also included a swap channel pos.15 from the proposed compressor-starter, in order to give the engine the best, in combination with efficiency, dynamic properties (not critical).

The engine starts with the start system. The proposed starter compressor or from the air accumulator through the start channels pos.16 through the check valves pos.17 and openings in the center of the bottoms of the compressors K1 and K2, the compressed air is pumped into the maximum pressure zone of the traction engines D1 and D2. At the same time, fuel is injected and mixed with air through the nozzle pos. 18.

The resulting working fluid is ignited by a spiral of constant glow pos.19. Directional expanding oncoming flows are broken apart, while additionally mixing. At the time of increasing pressure in the maximum pressure zone of the reciprocating screw blocks, the starting channels are blocked by check valves pos.17. In this case, a short-term supply of compressed air through the pumping channels, pos. 15, into the intercoil space of the compressors is possible. The resulting pressure through the spiral wall of the movable auger drives the bottom of the movable auger and crankshafts through the jumpers and disks of the movable auger. The exhaust gases are discharged through the nozzles pos.20. At the same time, compressors connected with the crankshaft come into motion, the air into which flows through the nozzles of pos. 21 and, by the screw blocks of the movable working chambers of the mechanical compression of the compressors, are pressed into the maximum pressure zone. With an uninterrupted supply of fuel, the duty cycle closes.

Axial reciprocating rotary screw type oil pump.

The operation of a reciprocating rotor-type screw unit along with relative oscillation is accompanied by the simultaneous rotation of both screws in a common housing.

In the presented model of the axial, reciprocal screw oil pump of a rotary type of a subgroup. 4.2 of the graphic part, the spiral walls have a one and a half turn winding. The resulting intermediate volume is assumed not so much for slight compression as for use as a buffer between zones with different pressures. The bottom of pos. 1'.1 of the driven screw slides with the outer surface in the corresponding housing bed of pos.22 and is held in the desired spatial position due to the annular guides of pos.1'.5 included in the corresponding annular grooves of the housing. Seals pos.23 are intended for complete sealing. When the shaft pos.5 rotates through the pins pos.2.7, the torque is transmitted to the drive screw pos.2. At the same time, through the bevel gear, pos. 1.6 of the driven screw, meshed with the bevel gear, pos. 2.6 of the lead screw, through the pins of pos. 1.7, the driven screw pos. 1 'is rotated. Gear ratio is one. In this way, the variables of wedging and slipping characteristics of the points of convergence and divergence of the spiral walls are replaced. The oil entering through the pipe pos.24 is captured by diverging spiral walls pos.2.2 of the lead and spiral walls pos.1'.2 of the driven augers. After a complete revolution, the formed working volume is closed and crushed along the spiral arc by the same converging spiral walls. The oil squeezed out of the spiral assembly is ejected through the pipe pos. 25.

Across the whole range of their characteristics, the rotary axial reciprocal screw oil pump is fully comparable with the widely used axial piston pump. But unlike its closest analogue, the described model, due to the resulting centrifugal (and in the jet engine mode) effect, allows a lower accuracy class in the assembly of screws.

The combustion chamber of the reciprocating auger block of the engine part of the engine with a partially closed thermodynamic cycle and combined fuel.

The casing pos. 26 of the combustion chamber of the reciprocating auger block of the engine ICE engine part with a partially closed thermodynamic cycle and the combined fuel of the graphic part subgroup 4.3 is combined with the bottom of the auger of the reciprocating auger engine block from the passage opening with the possibility of feeding combustion products to the movable working chambers. Mutually, the auger block has a winding of spiral walls sufficient to condense water vapor. The process of its operation is provided by a reciprocating screw compressor supplying compressed air, a fuel pump supplying liquid fuel, a piston pos. 28 supplying solid fuel pos. 27, and a reciprocating screw pump supplying water through a heat exchanger pos. 29. The spiral pos. 19 of constant glow maintains combustion.

In the process, the fuel is mixed with compressed air and burns in the area of the constant heating coil, supporting the combustion of solid fuel. Expanded combustion products enter the movable working chambers of the engine part. At the same time, the water supplied through the heat exchanger towards the hot stream is heated and with steam formation, enveloping the hot products of combustion on the walls of the housing of the combustion chamber, also enters the movable working chambers of the engine part. During the movement of the working chambers, steam and combustion products are intensively mixed, accelerating heat transfer. At the exhaust of the engine part under atmospheric pressure, the exhaust steam cools and is brought to complete condensation with separation from the exhaust gases in the unit for condensing water vapor and separating the exhaust gases. The simplest unit of condensation of water vapor and separation of exhaust gases is presented as a gate heat exchanger, structurally similar to the exhaust pipes of cars.

The temperature in the engine part is maintained due to the ratio of the amount and temperature of water vapor and combustion products in the combustion chamber.

A method of manufacturing a spherical spiral wall of a spherical screw.

A method of manufacturing a screw involves cutting bodies of rotation or casting, followed by cutting the body of rotation. If the production of flat augers is possible on widespread existing equipment, starting from a lathe, then spherical ones require the use of special equipment.

The mathematical description of the whole complex of possible spiral walls comes from the general arc equation in an arbitrarily large number of dimensions, where the arc equation is presented as a system of time dependence of each measurement. That is, the moment will determine the position of the point in the "Cartesian" coordinate system. Below is a general view where:

X; Y; Z; ...; N - measurement values (coordinate axes);

Fx; Fy; Fz; ...; Fn - relative time characteristics (rate of change of processes);

t is the moment that changes as time.

System of variables. Here the equation takes the form:

As shown, the variable system allows in the current process, when changing the position of a point, to change the function itself. It is also possible to change the position of this function. Moreover, the position of the function is determined by the initial constants or the “free coefficient", which can be specified as a second-order function with a second-order moment. These second-order functions are set in place of the original constant or “free coefficients” by independent modules (blocks). The totality of all possible positions of a point, taking into account both the functions of the first and the functions of the second order in three dimensions, will give the surface. In fact, it looks like the movement of a generatrix path along a generatrix of a second order trajectory (for example, a plane is obtained by moving one straight line along another that intersects its straight line), that is, the ordinal functions are derivatives of this system.

Note: Reducing the moments of the first and second orders to a single moment by setting the relationship between them in this case does not make sense. Here we note that the second-order generator is not the second derivative of the spiral wall. In this case, the first derivative of the spiral wall is the arc of the spiral, and the second derivative is the tangent line. The latter is not an absolute statement of mathematical analysis, but is sufficient for work and terminology.

The described mathematical approach is proposed both for complete ideas about spherical walls and their manufacture, and as the basis for the "Computer Aided Design" (CAD) and is not the main task of the work. Therefore, the description is limited to the construction of an arc of a spiral in space.

The view of the system of variables of a spherical spiral in volume (a special case when the axis of the direction of formation of the arc of the spiral coincides with the Z axis)

Where:

R is the constant radius;

Vxy ° - the rate of change of the angle of rotation of the projection of the radius in the XY plane;

Vz ° - rate of change of the angle of rotation of the radius to the Z axis;

cos (∠Z ° o + Vz ° t-180 °) - projection of the radius on the XY plane;

t is the moment, changed as time;

cos (∠x ° o-Vxy ° t) cos (∠y ° o + Vxy ° t) - the projection of the projection of the radius onto the XY plane on the X and Y axis;

∠x ° o, ∠y ° o - the angles between the projection of the radius on the XY plane and the X and Y axes in the initial position;

∠Z ° o is the angle between the radius and the Z axis.

The requirements for equipment for the manufacture of spherical spiral walls of spherical screws exactly repeat the mathematical description of spherical spirals. The spherical workpiece must rotate in relation to the cutter in two directions, with a clearly established ratio of the speeds of these rotations. At the same time, the cutting edge of the cutting tool (preferably a milling cutter) is a second-order function. In group 5 of the graphic part in Fig. 32, the manufacturing principle of one spherical screw is shown, and in Fig. 33 of another spherical screw. The plane of pos. 30 arrow shows the direction of rotation of the workpiece around the axis of pos. 31. The plane of pos. 32 of the arrow shows the direction of movement of the rotary cutter of pos. 34 around the axis of pos. 33. The result of the trajectory pos. 35 of the movement of the cutting edge of the cutter will be a spherical spiral wall. On Fig shows the cutting edge as forming a second order for the mills of Fig 32 and Fig. 33.

Claims (24)

1. The reciprocating auger block of the movable working chambers of mechanical compression or using the pressure of a compressed liquid and / or gaseous working fluid includes one screw, combining one longitudinal end face of the spiral wall with a bottom with a through hole along the axis of the direction of formation of its spiral wall and a radius of not more than a distance from this axis to the nearest point of this spiral wall, and another screw, combining the opposite longitudinal end of the other spiral wall with the bottom, the width of the spiral groove of one screw a earlier than the thickness of the spiral wall of the other screw, the spiral walls of both screws have at least one full turn, the spiral wall of one screw is located in the spiral groove of the other screw, the spiral wall of one screw is rotated 180 ° along the axis of the formation of the spiral wall relative to the spiral wall of the other screw, in the working the position of the screws, the spiral walls in the places of convergence and divergence have constantly changing slipping points and constantly changing wedging points, the space between the bottoms of both shn kov is divided by spiral walls into sealed chambers, the chambers being located on both sides of any spiral wall, the spiral wall of one screw is capable of simultaneously rolling in two directions with its two spiral surfaces, slipping along two spiral surfaces of the spiral wall of the other screw, thus displacing spirals along the arc and at the same time changing the volumes of chambers that appear, form and cease in the space between the bottoms of the chambers and at the same time vibrate the whole screw and, in particular, the limit to ntour of its bottom against the background of the limit contour of the bottom of the other auger along an arc of a circle, characterized in that the working position of the augers with the possibility of working movement is provided by a clamping device and / or a converting drive, the augers have a spherical or flat design, spiral walls and spiral grooves of both augers have identical generatrices of the spiral, forming a second order of the spiral surface of the spiral wall of one screw identical to the generatrix of the second order of the spiral wall of the spiral groove of the other some, the free longitudinal ends of the spiral wall of one screw have the shape of the bottom surface of the trough of the other screw, the spiral walls of both screws have a uniform constant height, the spiral walls together with their bottoms of both screws are deflected by half-step offset of the spiral minus the sum of the thicknesses of both spiral walls, the limit the contour of the bottoms of the screws is made round, in the process of operation of the reciprocating screw block, a liquid or gaseous working fluid is compressed as much as possible in the area of the passage opening, the compression ratio of which decreases as the working chambers move to the periphery from the axis of the direction of formation of the spiral walls and having the smallest compression of the open chamber in the region of the limit contour of the bottom, presses, creating a liquid or gaseous pillow, on the bottom surfaces of the screws, while reducing pressure with the possibility of complete cessation, and the friction force of the spiral wall of one screw on the bottom of the other screw, which are inversely proportional to the pressure of the working fluid and directly proportional to the gravity of the screw and the gravity of the slide parts of the pressure device and / or conversion drive. 2. Mutually auger block of movable working chambers according to claim 1, characterized in that, having a spherical shape, the screws have axial relative displacement by deviation. 3. Mutually auger block of movable working chambers according to claim 1, characterized in that, having a flat design, the screws have a radial relative displacement by deviation. 4. Mutually auger block of movable working chambers of claim 1, characterized in that in order to balance the pressure of the working fluid on the bottom of one screw and to ensure that the spiral wall of one screw is in the spiral groove of the other screw, the free side of this bottom is combined with a similar spiral wall and provided its similar reciprocal spiral groove of the additional screw fixedly connected by jumpers with another screw, moreover, either an additional screw or a screw without a passage is provided with an additional through hole holes, or both of these screws. 5. Mutually auger block of movable working chambers according to claim 4, characterized in that it has a flat design, while the pressure of the working fluid on the screw bottoms is compensated by the pressure of the pressure plate of the pressure device, combined by jumpers of the pressure device with one screw, directly on the free side of the bottom another auger, or jumpers combined with another auger, or ring disks combined with another auger. 6. Mutually auger block movable working chambers according to claim 5, characterized in that between the clamping disk of the clamping device and the clamping elements combined with the bottom of the other auger, clamping bearings are installed. 7. Mutually auger block of movable working chambers according to claim 5 or 6, characterized in that the jumpers of the pressing device are configured to adjust the distance from the pressing disk of the pressing device to the screw with which it is fixedly connected. 8. The reciprocating auger block of movable working chambers according to claim 1, characterized in that the relative working position of the screws with the possibility of relative oscillation of the screws along the circular arc is fixed by the offset principal surfaces of the rotatable converting carriage through the repeated surfaces of the circular limit circuits on the ring disks combined with the jumpers with jumpers moreover, the annular disks are at the limit or moved outside the dimensions of the reciprocating auger block of the movable working chambers. 9. Mutually auger block of movable working chambers according to claim 8, characterized in that rolling bearings are installed between the repeated surfaces of the limiting round loops and the principal surfaces of the rotatable conversion carriage. 10. Mutually auger block of movable working chambers according to claim 8 or 9, characterized in that, having a spherical shape of the execution of the screws, the repeated surfaces of the limiting circular contours on the ring disks and the principal surfaces of the rotatable converting carriage are axially displaced planes. 11. Mutually auger block of movable working chambers according to claim 8 or 9, characterized in that, having a flat form of execution of the screws, the repeated surfaces of the limiting round contours on the ring disks and the principal surfaces of the rotated converting carriage are radially displaced cylinders. 12. Mutually auger block of movable working chambers according to claim 8 or 9, characterized in that, having a flat form of execution of the screws, two converting drives are used. 13. Mutually auger block of movable working chambers according to claim 11, characterized in that a crankshaft is used as a conversion carriage. 14. Mutually auger block movable working chambers according to item 12, characterized in that the crankshafts are used as converting carriages. 15. Mutually auger block of movable working chambers according to claim 1, characterized in that the relative working position of the screws with the possibility of relative oscillation of the screws along a circular arc is fixed in a common housing with the possibility of simultaneous rotation, with each screw rotating relative to its own axis of formation direction. 16. Mutually auger block of movable working chambers according to clause 15, wherein the screws are interconnected by a block of gears with a final gear ratio equal to one. 17. Mutually auger block movable working chambers according to claim 1, characterized in that with an increase in the number of turns of the spiral walls of the screws, the pressure difference between the working fluid in the emerging working chamber and the working fluid in the ending working chamber increases. 18. Mutually auger block of movable working chambers according to claim 1, characterized in that, for the purpose of cooling, lubricating or supplying a working fluid from the side of the movable auger, the mutually auger main block is supplemented with an additional mutually auger block, and both mutually auger blocks have a single converting drive, and the flow of lubricating or cooling fluid or working fluid from the additional reciprocal screw unit is carried out from the side of its movable screw through the channels into the cavity in the bottom of the movable screw of the main reciprocal screw Vågå block. 19. Mutually auger block of the movable working chambers according to claim 18, characterized in that the free side of the bottom of the movable auger of the main reciprocal auger block is used as the bottom of the movable screw of the additional reciprocal screw block. 20. Mutually auger block of movable working chambers according to claim 18, characterized in that it has a spherical shape and the additional and main reciprocal screw blocks are arranged so that the spherical bottoms have a single center of spheres. 21. Mutually auger block of movable working chambers according to claim 1, characterized in that used as the basis of the motor part in the internal combustion engine in its design includes a combustion chamber, the housing of which is combined with the bottom from the side of the passage opening and makes it possible to supply combustion products to movable working chambers, or which is arranged in the reciprocating screw unit itself, taking into account the mobility of the spiral walls and whose operation is ensured by gaseous, or liquid, or solid, or combination feed devices fuel, compressor and compressed air supply channel and ignition system. 22. Mutually auger block of movable working chambers according to item 21, characterized in that the spiral walls and / or the bottoms of the augers and / or the combustion chamber are provided with heat exchange channels, as well as holes or nozzles for supplying a heated working fluid of a circular thermodynamic cycle to the movable working chambers. 23. A method of manufacturing a spherical spiral wall of a spherical screw consists in cutting a rotating spherical workpiece with a thickness of the spherical wall not less than the height of the spiral wall, the cutting edge of the cutting tool being simultaneously rotated around the center of the spherical workpiece, and the axis of rotation of the cutting edge of the cutting tool is perpendicular to the axis of rotation of the spherical workpiece and the complex reaches the movement of the cutting edge of the cutting tool in the body of the spherical workpiece along the first-order generatrix ka spiral wall and spiral groove. 24. The method according to item 23, wherein changing the second-order generatrix of the spiral wall and spiral groove by changing the shape of the arc of the cutting edge of the cutting tool.

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