WO2013109170A1

WO2013109170A1 - Three-dimensional spherical rotary machine

Info

Publication number: WO2013109170A1
Application number: PCT/RU2013/000032
Authority: WO
Inventors: Александр Владимирович ДИДИН; Илья Яковлевич ЯНОВСКИЙ
Original assignee: Didin Alexandr Vladimirovich
Priority date: 2012-01-18
Filing date: 2013-01-17
Publication date: 2013-07-25
Also published as: RU2012101510A; EA201300027A1

Abstract

Three-dimensional spherical machine comprising a body, a rotor and at least one working cavity formed in the rotor with a displacer and a heavy-duty sealing element mounted in said working cavity, which machine is characterized in that the synchronizing sealing element has a mechanism for synchronization with the displacer through an angle of revolution about the axis of the working chamber, which synchronization mechanism is arranged within one working chamber. This makes it possible to improve the characteristics of the three-dimensional rotary machine.

Description

Spherical volumetric rotary machine.

The technical field to which the invention relates.

The invention relates to the field of engineering, namely to volumetric rotary machines.

The level of technology.

Known spherical volumetric rotary machine (SORM) (PCT / RU2010 / 000672), having a spherical cavity in the body, a rotor in the form of a ball with an output shaft, two working cavities are made in the form of figures of rotation around the axis of rotation of the rotor, while between the working cavities partitions are formed having a constant cross section. In the housing, a circular groove extends along the surface of the spherical cavity. In the groove, with the possibility of rotation about the axis of the groove, a separator is installed in the form of a ring with two protrusions inside the spherical cavity. The separator protrusions divides the working cavity into the working chamber, interacting with the partitions through the sealing synchronizing elements (In SE). SSE is made in the form of a cylinder with a pine axis, cut by a longitudinal slot under the partition. The SSE axis is installed in the annular part of the separator located in the groove. Due to the symmetry of the working chambers with equal pressures around the axis of the SSE, the sum of the forces and moments from the side of the working fluid on the SSE is zero. The separator manages to unload hydraulically from forces on the part of the working fluid. The distorting moment of forces acting on the rotor is restrained by small forces in the radial bearings due to the spacing of the supports over a sufficiently large distance along the shaft. All borders between working chambers are condensed on platforms. All together creates the opportunity to obtain high pressures, high efficiency and high power density.

However, this SORM has the following disadvantages. The feed of one stage varies from zero to the maximum value. A combination of two steps fails to obtain a sufficiently uniform feed. The unevenness is ± 15%. With an increase in the number of chambers in one stage, this type of SSE ceases to be balanced in load and does not allow to obtain high pressure. Using SSE with other degrees of freedom worsens the tightness conditions of the working chambers (especially with small dimensions).

Another disadvantage is the uneven movement of the separator having a sufficiently large moment of inertia, which limits the speed of the SORM, especially with large dimensions. Partially responsible for increasing the moment of inertia is the placement of the SSE axis in the annular part of the separator, which increases its thickness at the largest diameter.

The objective of the invention is the creation of SORM with a more uniform feed / torque, with high specific characteristics and with high efficiency, preserving its qualities in a wide range of dimensions. An additional advantage is a very strong shaft, due to which high pressure and high feed can be obtained at the multi-stage version of SORM.

The objective of the invention is achieved in that in a spherical volumetric rotary machine comprising a housing with a spherical cavity, a rotor mounted in the housing with the possibility of rotation of at least one circular cavity made in the rotor, with a displacer and a sealing synchronizing element installed in it, moreover the working surface of the circular cavity is the surface of rotation relative to the axis of the circular cavity intersecting the axis of rotation of the rotor mainly at right angles, the attenuating synchronizing element is installed it is mounted with the possibility of performing rotational vibrations relative to the axis of the circular cavity, and the displacer is mounted to rotate relative to the axis of the displacer, intersecting the axis of rotation of the rotor at an angle, and the synchronizing sealing element is made in the form of two ears connected by a spherical circle located in the circular cavity with a pine tree .

The objective of the invention is achieved by the fact that in the machine the sealing synchronizing element has a synchronization mechanism with a displacer along the rotation angle around the axis of the circular cavity, placed within one circular cavity.

The objective of the invention is achieved in that in the machine, the synchronization mechanism is made in the form of at least one guide and a groove interacting with it. The objective of the invention is achieved in that in a machine containing a separator mounted for rotation around the axis of the displacer and containing at least one protrusion, which serves to install a displacer on it with

the possibility of rotation around the axis of the displacer.

The objective of the invention is achieved in that in the spherical cavity of the machine, at least one circular groove is made at an angle to the axis of rotation of the rotor, for installing the displacer support in it.

The objective of the invention is achieved in that in the spherical cavity of the machine, at least two circular grooves are rotated relative to each other around the axis of rotation of the rotor.

The objective of the invention is achieved in that the machine has a separator mounted for rotation around the axis of the displacer and containing at least one protrusion that serves to install a displacer on it with the possibility of rotation around the axis of the displacer.

The objective of the invention is achieved in that in the spherical cavity of the machine, at least two circular grooves are made, rotated relative to each other around the axis of rotation of the rotor.

The objective of the invention is achieved in that in a spherical volumetric rotary machine comprising a housing with a spherical cavity, a rotor mounted in the housing rotatably, at least one circular cavity, at least one elongated cavity, made in the rotor, with installed displacers, and the axis of the circular cavity intersects the axis of rotation of the rotor mainly at a right angle and is the axis of the elongated cavity, the synchronizing sealing element is installed with the possibility of making rotational REPRESENTATIONS relatively the axis of the circular cavity, and the displacers are installed with the possibility of rotation relative to the axis of the displacers, intersecting the axis of rotation of the rotor at an angle, and to improve the performance of the machine in the round cavity and in the elongated cavity, different types of displacers are installed

The invention is illustrated using the drawings.

Figure 1 presents in isometry a spherical volumetric rotary machine (SORM) with the half of the body removed.

Figure 2 presents the half of the body SORM.

Fig. 3 shows a rotor.

Figure 4 presents the displacer.

Figure 5 presents the sealing synchronizing element (SSE).

Figure 6 presents SORM with a separator.

7 shows a separator.

On Fig presents a displacer.

Figure 9 presents the displacer with the liner.

Figure 10 presents SORM with displacers mounted on the axis.

Figure 11 presents the body of the SORM with two grooves divorced along the corner.

On Fig presents SORM with two grooves.

On Fig presents the rotor of the two-stage SORM.

On Fig presents SORM with two grooves (appearance).

On Fig presents SORM with the passages of the working fluid along the rotor.

On Fig presents part of the rotor SORM, visible passages of the working fluid along the rotor.

On Fig presents SORM (without housing) with 6 displacers of another type, fixed in pairs on three arcs.

On Fig presents the assembly of two displacers, fixed rigidly on one arc.

On Fig presents SORM (without housing) with 4 displacers of two types, fixed rigidly on one arc.

On Fig presents an assembly of displacers of two types on the same arc. On Fig presents SORM (without housing) with SSE for displacers of two types. On Fig presents SORM (without housing) with the integrated SSE.

On Fig presents the combined SSE for SORM on Fig.

On Fig presents the SORM rotor in Fig.22.

Description of the best sample.

Geometric axes that match during assembly are identified by the same numbers.

Spherical volumetric rotary machine (SORM) (figure 1) contains a housing 1, a rotor 2 with an output shaft 3, mounted in the housing 1 with the possibility of rotation around the axis of rotation 4 of the rotor 2, three displacers 5 mounted on the arcs 6 with the possibility of rotation around the geometric axis 7 intersecting axis 4 at an angle. The displacers 5 interact with the rotor 2 through the sealing synchronizing elements (U SE) 8.

The housing 1 (FIG. 2) has a spherical cavity 10, from which holes 11 exit for the shaft 3 to exit in opposite directions. Two circular grooves 12 under the arcs 6 extend along the surface of the spherical cavity 10. The geometric axis 7 of the groove 12 intersects the geometric axis 4 of the holes 11 at an angle (in this example, the angle is 35 degrees).

Symmetrically relative to the plane passing through the axis 4 perpendicular to the plane of the axes 4 and 7, there is an input window 14 of the working fluid. It is located on one side (in the figure below) relative to the plane passing through the center of the spherical cavity 10 perpendicular to the axis 4. The corresponding exit window 15 is located symmetrically with respect to the plane of the axes 4 and 7. It is centrally symmetrical to the first pair of entry windows 14 and exit 15 with respect to the center of the spherical cavity 10 is a second pair of windows of the input 14 and output 15. The grooves 12 are between the first and second pair of windows of the input 14 and output 15. The input window 14 smoothly passes into the inlet pipe 16. The output window 15 smoothly goes into the output oh branch pipe 17.

To increase the shoulder of the shaft support 3, on the housing 1 there are necks 18 extending the holes 11. For folding, the housing 1 is divided into two symmetrical halves. The plane of the connector passes through the axes 4 and 7. To connect the halves of the housing 1, on them, in the plane of the connector, there is a flange 19 on which the mounting holes 20 are made.

The rotor 2 (Fig.Z) is made in the form of a ball 22 on the shaft 3. In the ball 22 there are three circular cavities 23 open outward with a conical lateral side 24 and a spherical bottom 25. The geometric axes 26 of the circular cavities 23 pass through the center of the ball 22 perpendicular to the geometric axis 4, which is the axis of rotation of the rotor 2. The round cavities 23 are evenly distributed around the axis 4. In the center of the round cavity 23 there is a hole 27 coaxial to it.

The displacer 5 (Fig. 4) is bounded by a spherical convex surface 30, the radius of which corresponds (to within tolerance) to the radius of the spherical cavity 10, a concentric spherical concave surface 31 of smaller radius, two symmetrical sections 32 of convex conical surfaces that are large in angular extent, corresponding to the conical lateral side 24, the geometric axes 33 of which intersect in the center of the surface 30, and two symmetrical portions of 34 concave conical ited having a common geometrical axis 35 intersecting the axis 33 in the center of the surface 30 at right angles.

Through the entire surface 31, coaxially to the sections 34, there are two grooves 36.

The displacer 5 is connected on the surface 30 with two arcs 6. The arc 6 is a flat sector of the ring, concentric surface 30, the plane of which is parallel to the axis 35. The arcs 6 start approximately in the center of the surface 30 and go in opposite directions. The total angular length of the arcs 6 is slightly less than 240 degrees. The distance between the planes of the arcs 6 is equal to the distance between the grooves 12.

SSE 8 (Fig. 5) is made in the form of two symmetrical ears 40, symmetrically connected by a relatively thin spherical circle 41. Circle 41 has a physical axis 42 extending to the center of the sphere of circle 41. Ears 40 are placed on one edge of circle 41 (on its convex spherical surface) and are limited to the concentric circle 41 by a convex lateral surface 43 made in the form of a conical a surface corresponding to a conical side 24, concentric to a circle 41 with a convex spherical surface 44, corresponding to a spherical cavity 10. The inner side 45 of the ears 40, with which they are turned towards each other, is bounded by a convex conical surface, axis 46 which passes through the center of the sphere of the circle 41 perpendicular to the geometric axis 47 of the circle 41. Closer to the center of the circle 41, two guides 48 pass along its surface concentrically to the surfaces 45. For the convenience of processing, they and eyut planar side surface and a spherical convex surface. To unload SSE 8 from forces acting on the part of the working fluid, through-hole (radial) holes 49 of small diameter are made in a circle. In the ears 40, for unloading the SSE 8 from the forces acting on the side of the working fluid, holes 49 are also made along the radius of the surface of the inner side 45.

From the circular cavities 23 of the rotor 2 installed in the housing 1, SORM working cavities are formed, which are divided into two working chambers by a displacer 5 and a SSE 8. In Fig. 1, a working chamber 50 is seen to increase in volume, a working chamber 51 to decrease in volume, the working chamber 52 of the minimum, almost zero volume, the working chamber 53 of the maximum volume (the rotor 2 rotates clockwise when viewed from above).

Compared with the analogue, the ears 40 located in the same circular cavity 23 are interconnected by a spherical circle 41 located in the circular cavity 23 and having an axis 42 that receives the load from the ears 40. By means of the circle 41, the ears 40 are connected to the guides 48 through which the orientation of SSE 8, which is required at every moment, is provided. Two grooves 12 allow each displacer 5 to have support on arcs 6, occupying a considerable angular extent around axis 7 (almost 240 degrees), which allows the center of pressure of the working fluid on displacer 5 to be positioned between the support sites of the arcs 6 on the plane of the grooves 12 (for small angular dimensions of the arcs 6 of one displacer 5, its pressure center would be outside the reference area of the arcs 6 on the plane of the grooves 12, which leads to concentration of loads and an increase in friction losses). The connection (in the angle of rotation of the SSE 8 around the axis 26) of the displacer 5 with the SSE 8 through a pair: groove 36 - guide 48, allows them to have reliable synchronization within the same circular cavity 23. The SSE of different circular cavities 23 may not depend on each other. This fact makes it possible to have an arbitrary number of round cavities on rotor 2. The maximum feed can be obtained with two or three round cavities 23 per ball 22. A slightly lower feed is obtained with four round cavities 23 per ball 22. Moreover, in general, uniformity the feed increases with an increase in the number of round cavities 23, but with similar amounts of round cavities 23, uniformity is greater with an odd number of round cavities 23.

The front end of the arc 6 is not attached to the displacer 5 (the attachment point is closer to the middle of the arc 6), therefore, due to the elasticity of the material, it can deviate from its equilibrium position by a small amount. Such a deviation contributes to the appearance of a liquid wedge when the arc 6 moves along the groove 12. This requires that the thickness of the arc 6 be a little (usually of the order of 0.04 mm, but depends on the size of the SORM) less than the size of the groove 12 in this direction and the presence of a lead chamfers or fillets.

SORM has a feed / torque unevenness of ± 8.8% (for a given tilt angle of 12) and a feed rate of 2.0 cubic units per shaft revolution with a unit cavity radius of 10.

SORM as a pump operates as follows. When the rotor 2 is rotated uniformly around axis 4, the displacers 5 slightly rotate around axis 7. Due to the inclination of the axis of rotation 7 of the displacers 5 to the axis of rotation 4 of the rotor 2 (or, in other words, the plane of the grooves 12 to the plane of rotation of the rotor 2), relative to the rotor 2 displacers 5 move along the circular cavity 23, making rotations about axis 26 together with SSE 8 and turns about axis 35 of SSE 8. Moreover, rotor 2 through the interaction of the hole 27 with axis 42 (or side wall 24 with surface 43) and, further guides 48 with grooves 36 moves the extrusions spruce 5 around axis 7 along grooves 12. Orientation of SSE 8 in a circular cavity 23 is provided by the transmission of torque (angular position) by displacer 5 from grooves 12 through arcs 6 to guides 48 of SSE 8. Rotations of displacer 5 around axis 35 of SSE 6 are ensured by the interaction of the planes of arcs 6 with groove planes 12. Due to the rotation of the displacer around the axis 35 changes the size of the working chambers, into which the displacer 5 with SSE 8 divides the circular cavity 23. So the chamber 50 increases its size and the working fluid enters through the window 14 of the entrance of the working fluid from the inlet pipe 16, and the camera 51 reduces its the size and the working fluid exits from it through the window 15 of the exit of the working fluid into the outlet pipe 17. The chamber 52 has reached a minimum size equal to zero. Camera 53 has reached its maximum size. The chambers 52 and 53 at this moment are not connected with the windows of the entrance 14 and exit 15. The pressure force acting on the displacer 5 from the side of the working fluid is transmitted to them through arcs 6 in the plane of the grooves 12. The pressure force acting on the SSE 8 lies on the axis 42 and to the bottom 25. The friction moment relative to axis 24 is mainly compensated by the moment of forces transmitted to the SSE 8 through the guides 48 and the grooves 36. The forces and moments of inertia arising from the uneven rotation of the displacer 5 and the SSE 8 are also balanced in the same ways .

With three circular cavities 23 per ball 22, the axial load on the rotor 2 on average for the period is zero. However, it changes sign several times (three times) during the period. Alternating helps to improve the lubrication of thrust bearings: falling into the gaps on ball 22 or in the thrust bearing during lack of load (when the action of forces from the working fluid increases the gap), the fluid does not have time to leave the gap (for example, between the ball 22 and the surface of the spherical cavity 10) in the loaded area and serves as a hydraulic cushion.

This SORM, in comparison with the analogue, has the ability to change the working chamber to zero, which reduces losses when working with compressible working bodies (for example, when working with high pressures) and allows you to work effectively as a compressor. The compressor flow is higher, compared with the analogue, due to the absence of stray volume. To operate as a compressor, exit windows 15 are of a smaller angular size. In this case, in the chamber 51, cut off from the inlet window 14, a precompression chamber is first formed, and only when the working fluid reaches the outlet pressure (or when the volume decreases by a specified number of times), the chamber 51 enters the exit window 15. On the arcs 6, unloading grooves 37 can be located. The grooves 37 located on the upper plane of the arc 6 are joined by holes 38 extending through the displacer 5, with a chamber located on the opposite side (down) from the arc 6, and vice versa, the grooves 37 located on the lower the plane of the arc 6, joined by holes 38 going through the displacer 5, with a camera located on the opposite side (up) from the arc 6 to create a hydrostatic discharge of the arcs 6 and the displacer 5.

The execution of the SORM in FIG. 6 is generally similar to the SORM in FIG. 1. The difference is that in order to reduce the inertial loads from the displacers 5 on the SSE 8 and the pressure of the displacers 5 on the walls of the spherical cavity 10 due to centrifugal forces (friction losses are associated with it), the arcs 6 of the displacers 5 are combined into a separator 60. The separator 60 (Fig. 7) is made in the form of a flat ring 61 with three symmetrically located flat protrusions 62 directed to the center of the ring 61. The ring 61 with the protrusions 62 is bounded by flat ends 63. The convex spherical surface serves as the outer side 64 of the ring 61. Between the protrusions 62, the ring 61 is bounded by a concave spherical surface 65. The surface 66 of the protrusions 62 facing the center of the ring 61 is also spherical. Surfaces 64, 65, 66 are concentric. The ends 67 (in an angle around the axis 7) of the protrusions 62 are bounded by flat areas. At the ends 67 there are openings 68 for installing damping elements. The protrusions 62 in turn "lead" (create the main traction force) divider 60 along the groove 12.

Another difference is that the spacer 60 is mounted in the housing 1 to form a rolling bearing. At the ends 63 of the ring 61 there are tracks 69 of a rolling bearing. In the housing 1, on both sides of the groove 12, circular grooves 70 are made, open in the cavity of the groove 12 and serving to accommodate balls 71 (Fig. 6) of the bearing elements of the rolling bearing and as tracks of this bearing.

The displacer 5 (Fig. 8) differs from the displacer 5 (Fig. 4) in that almost along the entire surface 50, there is a symmetrical flat, deep, but not through groove 74 under the protrusion 62. The groove 74 is slightly larger in angular length than the angular length protrusion 62. On the surface of the protrusion 62 for unloading the displacer 5 from the pressure drop from the side of the working fluid, discharge grooves 76 are made to which holes 77 lead through the displacer 5 from sections 32.

Damping elements absorb possible impacts when changing the leading protrusion 62. In the absence of a damping element, its role is played by the resistance of the working fluid partially locked (with a certain degree of tightness) in the groove 74.

Instead of the rolling bearing, the arc 6 of the spacer 60 can operate as a sliding bearing, similarly to the example in FIG. 4.

In this design, a large part of the circular cavity 23 is blocked by the protrusion 62 of the separator 60. Due to unloading, the displacer 5 covers a small part of the area adjacent to the ends 67 of the protrusion 60 and to the surfaces 66. The area covered by the SSE 8 is also small. Therefore, the main load from the pressure drop of the working fluid lies on the separator 60, and the displacer 5 and SSE 8 are less loaded. Since the spacer can have sufficient support (a large rolling bearing or, as in the example of FIG. 1, a sliding bearing with hydraulic unloading), the SORM can operate with a large pressure drop.

Compared with the analogue, this design allows to reduce the mass of the arc 6 located outside the radius of the spherical cavity 10 (the SSE axis is not placed in it), which reduces the moment of inertia and, consequently, the inertial load from the displacer 5, allowing SORM to work at high speeds.

Compared with the analogue, this design has a thicker (volumetric) part of the displacer 5 located in the spherical cavity 10, which allows not only to remove the parasitic volume, but also while maintaining strength (since a thick beam holds a greater load on the deflection than thin of the same mass) to fill it from a lighter material. The effect of using a lighter material for the displacer 5 reduces the inertial load on the friction pairs displacer 5 - SSE 8 - rotor 2 by reducing the inertia of the displacer 5. The grooves 36 can also be performed on the SSE 8, and the guides 48 can be performed on the displacer 5. With a large number of grooves 36 and guides 48, the grooves and guide protrusions become indistinguishable, since the partition between two grooves can be regarded as a guide protrusion and vice versa, the space between two guides can be regarded as a groove. The grooves 36 and the guides 48 may be from one to a sufficiently large number, depending on the manufacturing technology. In this sense, the guide pair 48 — groove 36 is the synchronization mechanism of the displacer 5 with the SSE 8 by the angle of rotation around the axis 26 of the round cavity 23, which was able to be placed inside the sphere of the spherical cavity 10 and, thereby, reduce the inertial load from the arcs 6.

For assembly, the two parts of the displacer 5 adjacent to the groove 74 are made in the form of liners 80. The liner 80 has an angular length along the groove 74 approximately equal to the angular length of the protrusion 62. At the place of the liner in the displacer 5, a cavity 81 is formed, expanding the groove 74. It is fixed liner 80 with pin / screw through hole 82.

When assembling, in the round cavity 23 of the rotor 2 are installed SSE 8 and displacers 5 without liners 80 (for example, all are shifted to one side along the shaft to the stop). In this position, the separator 60 can be worn on the rotor 2. Its protrusions 62 fit into the grooves 74 of the displacers 5 using the adjacent cavities 81. The liners 80 are installed in the cavity 81. The rotor 2 assembly with the liners 80 and the separator 60 is installed in the housing 1 At the same time, balls 71 (6) with separators are installed in the grooves 70. The thus formed ball bearing senses a warping moment of forces acting on the separator 60 from the side of the working fluid.

The execution of the SORM in Fig. 10 is generally similar to the SORM in Fig. 6, but instead of the arcs 6, the displacers 5 are mounted on the physical axis 85. The axis 85 receives a distortion moment acting on the displacers 5. For this, the protrusions 62 instead of the ring 61 are attached to the bowl 86, executed in the form of a relatively thin-walled hemispheres with through holes 87 for the passage of the working fluid to the windows of the entrance 14 and exit 15. The bowl 86 is made coaxially with the axis 85.

Instead of a groove 12, there is a recess 88 under the bowl 86 in the spherical cavity 10 in the housing 1. One of the holes 11 is aligned with the axis 7. To fix the halves of the housing 1, the bushings 89 are pressed onto the necks 18.

The rotor 2 has only one output shaft 11.

When performing two symmetric round cavities 23 on the ball 22 (not shown in the figures, since it is a special case of SORM in Fig. 1 or Fig. 6), displacers 5 are rigidly attached to one arc 6 in the form of a ring 60 or to several such parallel arcs 6 (as in the SORM version of FIG. 1), or are mounted on the splitter 60 (as in the SORM version of FIG. 6). At the same time, to compensate for the axial load, SSEs 8 from two round cavities 23 can be connected together, for example, along the axes 42. The delivery of such a SORM with one ball 22 (with one step) will pulsate from zero to maximum.

To align the feed of one stage 90 SORM, in the housing 1 (11) there are two grooves 12, rotated relative to each other around axis 4 by an angle φ. The arc 6 of the displacer 5 of one circular cavity 23 is located in one groove 12, and the arc 6 of the displacer 5 of the other round cavity 23 is located in another groove 12. The arc 6 has an angular length of slightly less than 180 degrees. Moreover, despite the fact that the round cavities 23 are displaced in this example by half a revolution around the axis 4 relative to each other, due to the rotation of the grooves 12, the displacers 5 are phase-shifted relative to each other by an angle of 180 + φ (or 180-φ) .

When displacer 5 is displaced in phase by 180 degrees, two working chambers located centrally symmetrically operate in one phase (in phase, for example, maximum expansion speed) and two in antiphase to them (for example, maximum compression speed), so the sum of feeds has a ripple (from 0 to 2x maximum).

When performing a two-stage SORM (Fig. 12), the grooves 12 in one stage 90 and in another stage 91 are parted (rotated around axis 4) by cp = 45 degrees (so we get the windows of the entrance 14 and exit 15 of a larger size), the cases of the 1 stages are mirrored, and the rotors of the 2 stages are rotated 90 degrees relative to each other about the axis 4. Then the supply of the working chambers 50, 51 will be uniformly distributed in phase, and we will get less ripple total feed.

When the grooves 12 are opened for timely communication of the working chambers 50 and 51 with the input and output windows 14 and 15, the rotor has a bypass circle 92 mounted coaxially on the shaft 3. Two bypass circles 92 are made for one spherical cavity 10 (one on one side of the ball 22, the other on the other hand). The inner surface 93 of the bypass circle 92 is a concave spherical surface - a continuation of the surface of the ball 22. The outer surface 94 of the bypass circle 92 is convex spherical. On the bypass circle 92, overflow windows 95 are filled. They are displaced in the round cavities 23 towards each other to compensate for the rotation of one of the grooves 12 (since the input and output windows 15 and 15 are common for the two round cavities 23, and the grooves 12 work with these round cavities 23 are rotated through an angle φ).

In the housing 1 in the spherical cavities 10 there are concentric axes 4 of the recess 96 under the bypass circles 92. In these recesses 96 the windows of the inlet 14 and the outlet 15 are filled.

To reduce hydrodynamic losses, the passages of the working fluid to the inlet windows 14 and the passages of the working fluid from the exit windows 15 are approximately tangential to the sphere of the spherical cavity 10 in the direction of the local speed of the rotor 2. To the inlet pipe (for different inlet windows 14 and different stages) 16 and to the common outlet pipe 17, channels in the form of approximately curved (adjusted for circumventing grooves 12) into the arc of the pipe 97 lead.

SORM has a feed / torque unevenness of ± 4.6% and a feed rate of 2 * 1.8 cubic units per shaft revolution with a unit cavity radius of 10.

When performing a single-stage SORM (one step of the previously shown 2-step SORM), the grooves rotate 90 degrees around axis 4. Then when one of the working chambers 50, one of the spherical cavities 10 will have a maximum expansion rate, the other chamber 51 will have a maximum compression rate, the change rate of the other two working chambers 52, 53 in the other round cavity 23 will be zero, and we will get a smoothed total feed of SORM with pulsations of ± 20% and a feed rate of 1.8 cubic units per revolution shaft with a unit radius of the cavity 10.

To align the inlet pipes 16 to the common inlet pipe 16 and, similarly, to combine the outlet pipes 17, in the SORM (Fig. 15) in the rotor 2 channels similar to the screw 98 are executed (Fig. 16) for the passage of the working fluid along the rotor 2. They come from the round cavities 23 (Fig. 15) from the side that is closer to one of the output shafts 3 to the places on the ball 22 closer to the other output shaft 3. Passing along the axis 4, the channels 98 make a half turn around axis 4. Then they exit to the surface in the form of bypass windows 95. The passage of the working fluid from the chambers 50, 51 closest to this place, also formlen as windows 95. The windows 95 are evenly spaced circumferentially about the axis 4.

Arcs 6 are in the same groove 12 and, to increase their angular length, partially overlap each other.

SORM (Fig. 17) contains a housing 1, a rotor 2 with an output shaft 3, mounted in the housing 1 with the possibility of rotation around the axis of rotation 4 of the rotor 2, six displacers 105 mounted on arcs 6 with the possibility of rotation around the geometric axis 7, intersecting the axis 4 under angle. The displacers 105 interact with the rotor 2 directly and through the wheels 100.

The housing 1 is identical to the housing 1 of FIG. 2 with the exception of the number of grooves 12. It has three of them (by the number of arcs 6).

The rotor 2 is made in the form of a ball 22 on the shaft 3. In the ball 22 there are three elongated open cavities 123 with two conical sides 24 and a spherical bottom 25. The elongated cavities 123 have the shape of a trace of a truncated cone, which is rotated through an angle (in this example, ± 35 degrees) around axis 26, perpendicular to the axis 4 of rotation of the rotor 2. The geometric axis 26 pass through the center of the ball 22. The elongated cavity 123 is distributed evenly around the axis 4.

The displacer 105 (Fig. 18) is bounded by a spherical convex surface 30, the radius of which corresponds (equal to within tolerances) to the radius of the spherical cavity 10, a concentric spherical concave surface 31 of smaller radius, and a conical surface 101, whose geometric axis 102 passes through the center of the surface 30. To replace sliding friction with rolling friction (to increase the permissible load and reduce friction), part of displacer 105 is embedded in a separate element - wheel 100. Wheel 100 is installed coaxially with the rest of the displacement spruce 105 on the physical axis 104. The axis 104 rotates together with the wheel 100. In order to reduce the pressure drop, the wheel 100 is smaller along the axis 102 than the rest of the displacer 105 (since the rolling friction pair is capable of bearing a greater load than a pair of sliding friction - axis 104 - hole in the displacer 105 under the axis 104).

The displacer 105 is connected along the surface 30 with the arc 6. The arc 6 is a flat ring concentric to the surface 30. Two displacers 105 are mirror-symmetrically mounted on one arc 6.

Other pairs of propellants 105 are mounted on other arcs 6 parallel to this arc 6. The arcs are spaced along axis 7. The distance between the planes of the arcs 6 is equal to the distance between the grooves 12. The axes 102 of the displacers 105 are located in the same plane.

From the elongated cavities 123 of the rotor 2 installed in the housing 1, SORM working cavities are formed, which are divided into two working chambers by a displacer 105.

The disadvantages of SORM in Fig.1-16 and SORM in Fig.17 is a change in the angular distance between the displacers 5/105 of one stage. The distance can be constant only for two diametrically opposed 5/105 displacers. But such a pair of 5/105 displacers gives a flow pulsating from zero to maximum. This forces the installation of displacers 5/105 on separate arcs 6, which are the whole ring 61 or part of the ring 61 or movable relative to the ring 61, which complicates the design, makes it less durable.

It turns out that the combination of displacers 5 and 105 of the SORM in FIGS. 1-16 and the SORM in FIG. 17, installed in one stage (FIG. 19), gives several positive effects at once. Firstly, on one arc 6, it becomes possible to rigidly install up to 4 displacers 5 and 105 (two of each type), which increases the rigidity and reliability of fastening and allows you to partially compensate for the load on the arc 6 from different displacers 5 and 105, which reduces losses by friction. Secondly, it eliminates the need to synchronize SSE 8 with displacer 5 using guides 48 and grooves 36 (this reduces the complexity of execution and leakage). Thirdly, SSE 8 serves as the physical axis around which SSE 108 rotates. Fourth, elongated cavities 123 are successfully located on ball 22 in combination with cavities 23. Four elongated cavities 123 occupy a lot of space on the ball - their ends abut each other . Four circular cavities 23 occupy a lot of space on the ball - their midpoints abut against each other. A combination of round cavities 23 and elongated cavities 123 has a tight arrangement on the ball 22, and gives a large total feed in the same size of the spherical cavity 10. Fifth, a combination of round cavities 23 and elongated cavities 123 gives a more uniform feed than this same number of cavities of the same type.

Two displacer 5 (Fig.20) are located symmetrically relative to the arc 6 and mirror. Two displacers 105 are also symmetrically and mirrored, but the pair of displacers 105 is rotated 90 degrees about the axis 7 relative to the pair of displacers 5 (the arrangement may not be symmetrical with an asymmetric SSE 8). The axis 102 coincides with the axis 35. This arrangement makes the displacers 105 axes of the displacers 5.

To increase the tightness (Fig. 21), the displacer 105 may have a SSE 108, which is similar to a cone with an approximately square section, with a conical hole for it aligned with it. Two sides 109, working on the surface 24 have conical surface. It is also limited by extensions of surfaces 30 and 31. SSE 108 allows hydraulic discharge of the displacer 105.

To exclude grooves 36 (Fig. 22) and guides 48, two types of displacers 5 and 105 (Fig. 23) are combined into one (possibly prefabricated) part. One way is to combine the two types of SSE 8 and SSE 108 using arcs 112. On the rotor 2 (Fig.24) perform additional grooves 113 under the arc 112.

Claims

CLAIM

1. Spherical volumetric rotary machine, comprising a housing with a spherical cavity, a rotor mounted in the housing with the possibility of rotation of at least one circular cavity made in the rotor, with a displacer installed in it and a sealing synchronizing element,

moreover, the working surface of the circular cavity is the surface of rotation relative to the axis of the circular cavity intersecting the axis of rotation of the rotor

mainly at a right angle, the sealing synchronizing element is mounted with the possibility of performing rotational vibrations relative to the axis of the circular cavity, and the displacer is mounted with the possibility of rotation relative to the axis of the displacer crossing the axis of rotation of the rotor at an angle,

moreover, the sealing synchronizing element is made in the form of two ears connected by a spherical circle located in a circular cavity with a pineal axis.

2. The machine according to claim 1, characterized in that the sealing synchronizing element has a synchronization mechanism with a displacer at an angle of rotation around the axis of the circular cavity, located within one circular cavity.

3. The machine according to claim 2, characterized in that the synchronization mechanism is made in the form of at least one guide and a groove interacting with it.

4. The machine according to claim 1, characterized in that the machine contains a separator mounted for rotation around the axis of the displacer and containing at least one protrusion, which serves to install a displacer on it with the possibility of rotation around the axis of the displacer.

5. The machine according to claim 1, characterized in that at least one circular groove is made in the spherical cavity of the machine at an angle to the axis of rotation of the rotor, for installing the displacer support therein.

6. The machine according to claim 5, characterized in that at least two circular grooves rotated relative to each other around the axis of rotation of the rotor are made in the spherical cavity of the machine.

7. Spherical volumetric rotary machine, comprising a housing with a spherical cavity, a rotor mounted in the housing rotatably, at least one circular cavity, at least one elongated cavity, made in the rotor, with displacers installed therein,

moreover, the axis of the circular cavity intersects the axis of rotation of the rotor mainly at right angles and is the axis of the elongated cavity,

sealing synchronization element installed with the possibility

performing rotational vibrations relative to the axis of the circular cavity, and the displacers are installed with the possibility of rotation relative to the axis of the displacers crossing the axis of rotation of the rotor at an angle

moreover, to improve the characteristics of the machine, different types of displacers are installed in the round cavity and in the elongated cavity.