WO2011078744A1

WO2011078744A1 - Rotary volumetric machine

Info

Publication number: WO2011078744A1
Application number: PCT/RU2010/000773
Authority: WO
Inventors: Александр Владимирович ДИДИН; Илья Яковлевич ЯНОВСКИЙ
Original assignee: Didin Alexandr Vladimirovich; Yanovskij Ilja Yakovlevich
Priority date: 2009-12-22
Filing date: 2010-12-21
Publication date: 2011-06-30
Also published as: RU2009147347A; EA201001815A2; EA201001815A3

Abstract

A compact, easy-to-produce, multistage rotary volumetric machine is proposed comprising: a housing with a spherical chamber that has a circular slot around it; a rotor rotatably mounted in the housing and having at least one ball-like part with at least one baffle thereon, wherein the plane of the circular slot passes at an angle in relation to the axis of rotation of the rotor; and a divider with an opening for the ball-like part of the rotor and a slit for the baffle, said divider being mounted in the circular slot in such a way as to be capable of rotating in relation to the housing in the plane of the circular slot and projecting into the spherical chamber. In the housing chamber a working chamber is formed around the ball-like part of the rotor and is divided by the divider into parts in which the baffle moves by rotating with the rotor, thus forcing out the working medium. The rotor is provided with an inlet port on one side of the baffle and a working medium outlet port on the other side of the baffle. The entire passage of the working medium between the stages from the inlet to the outlet of the rotary volumetric machine is organized with the aid of two channels that pass inside the rotor throughout the entire rotor. The type of hydraulic connection between the stages is determined by flanges situated in the channels.

Description

Volumetric rotary machine.

The technical field to which the invention relates.

The invention relates to the field of mechanical engineering, namely to rotary volumetric machines that can be used as pumps, hydraulic drives.

The prior art.

Known ORM (patent RU 2376478), comprising a housing, the working surface of which is made as part of a segment of a sphere, a rotor with a working surface of rotation mounted rotatably in the housing, an annular concentric working cavity formed by the housing and the rotor, a separator made in the form of an inclined washers mounted motionlessly in the housing at an angle to the geometric axis of rotation of the rotor and dividing the working cavity into two parts, and at least one groove along its geome is made on the working surface of the rotor ternary axis of rotation, a piston is installed in the rotor with the possibility of overlapping (sealing) the working cavity and performing rotational vibrations around its geometric axis intersecting the geometric axis of the rotor, and the piston is made in the form of at least part of the disk, and each piston has at least one slotted seal sealing synchronizing element (SSE) for the passage of the separator.

This ORM has reliable synchronization, however, the maximum pressure maintained by one stage and the resource are limited by the wear resistance of the SSE – piston friction pair, since, due to the asymmetry of the load, the specific pressure in them is approximately equal to the differential pressure of the stage. The disadvantage is the presence of two pairs of windows of the entrance and exit of the working fluid on the housing of each stage, which must be connected by channels to bypass the working cavity.

Known ORM (patent RU 2202695) containing a stator, working chambers, a rotor mounted for rotation, a separator mounted for rotation, and the geometric axis of rotation of the rotor and the separator intersect at an acute angle, the entrance window and the exit window of the working fluid, and the separator is in meshing with the rotor through a sealing synchronizing element, cut in its middle part through a slot through which the entire rotor passes.

The disadvantage is the presence of two pairs of input and output windows of the working fluid on the housing of each stage. Moreover, to connect the input / output windows to each other, it is necessary to bypass a groove of large diameter located around the cavity of the housing for installing a separator in it. This increases the mass, size, and complexity of the ORM enclosure. Especially if you use two steps and have to connect eight windows. The disadvantage is the presence of a flat portion of the rotor passing through the slot in the sealing synchronizing element. It does not allow the channels for the working fluid to pass through the rotor, it limits the maximum working pressure and maximum torque that can be transmitted to the next hydraulically parallel stage of the ORM, which is required for obtaining an almost uniform feed.

Known ORM (patent GB 790190), comprising a housing, a rotor with a spherical part, mounted in the housing rotatably, and with at least six baffles on this spherical part, a sphere-shaped working cavity formed around the spherical part of the rotor, with an annular groove around her, a separator with an opening for the spherical part of the rotor, with the outer and inner part, having slots for partitions, installed by the outer part in the groove of this cavity, with the possibility of rotation relative to the housing in the plane of the groove, I protrude cabbage into the working cavity with the inner part, and interacting with the spherical part, and partitions with a separator divide the working cavity into working chambers formed on opposite sides of the separator. Slots have sliding seals in the slots to compensate for the changing (due to the inclination of the axis of rotation of the separator to the axis of rotation of the rotor) relative angular distance between the slots and their angular size, as required by the mating conditions. Two entry windows are located on the housing symmetrically with respect to the center of the sphere-shaped cavity on opposite sides of the separator and, similarly, two exit windows are located. Windows have direct access to the working cavity.

The disadvantage is the presence of a large number (two pairs) of windows located (in pairs) far from each other, because they have to be connected by long channels, bypassing the separator, whose diameter is larger than the diameter of the cavity, which significantly increases the size and weight of the ORM. Another drawback is the need to use sliding seals (reduce the maximum allowable pressure drops), which are required by nfs-using more than two protrusions on the rotor (and to maintain constant pressure of the ORM, at least three partitions are required when placing windows with access to the working chamber). In addition, the geometry of the mating surfaces of the partitions and sliding seals is not given, allowing the chambers to be sealed.

Known (~ since 1905) and other ORMs with a sphere-shaped working cavity and an annular groove made around it, having a rotor with baffles, mounted for rotation in the housing, and a separator installed with its outer part in the said groove with the possibility of rotation around the rotor relative to the housing . Between the working bodies they form symmetrical (or almost symmetrical) working chambers. Due to the symmetry of the chambers having high pressure, it is possible to balance the pressure forces from the side of the working fluid on many working bodies. The separator, due to the presence of the outer part located in the annular groove, can be completely unloaded hydraulically. Due to the sphere-like nature of the working cavity, ORMs have developed contact surfaces between the working bodies, which reduces the internal flow of the working fluid. Those. OPM of this type has the ability to obtain high pressures and high efficiency.

However, they did not receive distribution. The reason is the difficulty of supplying the working fluid to symmetrical working chambers located on both sides of the rotating separator. Usually, with an ORM consumer, the supply / withdrawal of a working fluid to the ORM is made in one place. Then in the ORM it is required to deliver the working fluid to the working chambers located centrally symmetrically in the working cavity. To bypass the working cavity to the opposite side, the minimum length of the trunk is required, taking into account the walls and diameter of the trunk, about 4R (R-radius of the cavity). Given the fact that it is necessary to bypass the groove for the separator and the sealed connector of the housing, about one or two R is added. As a result, a total length of the trunk of about 10R is required for the supply and removal of the working fluid. If OMP requires two steps for continuous supply, this number doubles. As a result, compactness, power density are lost on this and manufacturing is greatly complicated. So, the routing of pipelines by ordinary pipes, of sufficient cross-section for using the speed capabilities of the ORM, increases the diameter by -1.7 times, and the volume by ~ 5 times. The wiring holes in the case greatly complicates the case, and still significantly increases the size and weight. The objective of the invention is to provide a reliable, compact, technological ORM with a long resource, adapted to the operating conditions in the well. Those. Well the presence of abrasive in the working fluid, which varies in time with viscosity and temperature of the working fluid (from water to viscous oil). This implies the need to exclude highly loaded friction pairs (even when coated with wear-resistant materials) from the ORM design, use only surfaces with simple geometric shapes that are mated on platforms and accessible for machining as mating surfaces, as well as minimizing leakage lengths in each stage. In addition, to exclude vibrations of the entire installation, the ORM at the output should provide an almost uniform (non-pulsating) feed.

An ORM satisfying all of the above conditions was created on the basis of an ORM with a sphere-shaped working cavity and a separator rotating around the rotor relative to the housing.

The objective of the invention is achieved in that the volumetric rotary machine comprises a housing with a sphere-shaped cavity and a circular groove around it, a rotor with at least one spherical part, and a partition on it, mounted in the housing for rotation, and the groove plane extends at an angle along relative to the axis of rotation of the rotor,

side walls made entirely on either the rotor or on the housing, or partially on the rotor, partially on the housing,

a separator with working ends, an opening for the spherical part of the rotor and a slot for the partition, mounted in a circular groove, rotatable relative to the housing in the plane of the circular groove, protruding into a sphere-shaped cavity, and interacting with a hole with a spherical part, and working ends with side walls,

in the body cavity, around the spherical part of the rotor, a working cavity is formed, which the separator, when interacting with its working ends with the side walls, and with its hole with the spherical part of the rotor, divides into parts in which, due to rotation with the rotor, the partition moves, forcing out working fluid, and on the rotor on one side of the partition there is an entry window, and on the other side of the partition is the exit window of the working fluid.

The objective of the invention is achieved by the fact that in a volumetric rotary machine, the input and output windows are located on the surface of the spherical part of the rotor. The objective of the invention is achieved in that in a volumetric rotary machine for supplying / withdrawing a working fluid to the working cavity, a canoe is made inside the rotor.

The objective of the invention is achieved by the fact that in a volumetric rotary machine on a common rotor several steps are made, and the channels pass through all the steps, and between adjacent steps one of the channels is blocked by a plug.

The objective of the invention is achieved in that in a volumetric rotary machine, the input of the working fluid is made at one end of the rotor, and the output of the working fluid is made at the other end of the rotor.

The objective of the invention is achieved in that in a volumetric rotary machine in the slot of the separator is installed at least one power synchronizing element to improve the synchronization conditions of the separator with the rotor.

The objective of the invention is achieved in that in a volumetric rotary machine, a power synchronizing element, to increase the shoulder of the forces holding it, is attached with the possibility of rotation to the rotor using an axis.

The objective of the invention is achieved in that in a volumetric rotary machine, the power synchronizing element is made in the form of a cylinder cut from one end with a groove and having an axis hole passing through the groove for fastening to the rotor.

The objective of the invention is achieved in that in a volumetric rotary machine, the power synchronizing element is implemented in the form of a lever mounted in the rotor and passing to the separator through the input or output window of the working fluid.

This application is a continuation and development of the previous application RU 2009144853, which I include (for countries with this practice) in this application.

The invention is illustrated using the drawings.

Figure 1 presents an isometric view of a four-stage volumetric rotor machine (ORM) assembled in a pipe. For clarity, the proximal half of the pipe, the halves of the three parts of the body, end nuts and podshshshkah are cut off (removed). Sections are not shaded.

Figure 2 presents in isometric details of the body ORM in the same form as in fng. 1-

Fig. 3 shows an isometric view of the extreme part of the body.

Figure 4 presents in isometric middle part of the body.

Figure 5 presents in isometry the brightness of the housing. Figure 6 presents in isometry the rotor ORM. For clarity, a local cutout of ¹ A of the rotor shaft and the output half shaft was made, halves of one extreme and one middle ring were cut off. The sections are not shaded,

Figure 7 is a perspective view of the rotor shaft. A local cutout of ¹ A is made at its end, showing the location of the channels and plugs.

On Fig presented in isometric middle ring.

Figure 9 shows an isometric extreme ring.

10 is a septum isometric view.

11 is an isometric output half shaft. Made a local cut in 1/3. The cross section is hatched.

12 is a perspective view of a spacer.

On Fig presented in isometric power synchrotron element (SSE).

On Fig presents in isometric part of the rotor with the outer ring, middle ring, baffle and SSE bolted to the rotor.

On Fig presents in isometric part of the ORM according figL. The proximal halves of the pipe, parts of the casing, the extreme and middle rings, unloading rings and the separator are cut off.

On Fig presents in isometric middle part of the body with discharge grooves.

On Fig presents in isometric separator with holes for unloading.

On Fig presents in isometric separator openings for unloading and with another variant of the discharge grooves.

On Fig presents in isometric version of the power synchronizing element.

On Fig presents in isometric version of the separator.

On Fig presents in isometric part of the ORM with the fastening of the side parts of the walls on the housing. Cut off the halves of the parts of the housing, the separator and some rings. Sections are not shaded.

On Fig presents in isometric one-sided ring mounted on the housing.

On Fig presents in isometric version of the septum.

On Fig presents in isometric part of the ORM. A 1/3 local cutout is made in the rotor body itself; halves of the body parts and dividers are cut off. Sections are hatched. On Fig presents in isometric version of the partition, working in the ORM with one side wall attached to the rotor, and the other to the body.

On Fig presents in isometric version of the separator.

On Fig presents in isometric version of the septum.

On Fig presents in isometric section of the rotor with a plane perpendicular to the axis of rotation passing through the center of the stage, SSE, a partition, and a separator, to show the installation of the lever SSE in the rotor.

On Fig presents in isometric lever SSE. The near halves of its bearings are cut off.

On Fig presents in isometric part of a multi-stage ORM, consisting of two stages. The proximal half of the pipe is cut off. The near halves of the steps of the body are removed

On Fig presented in isometric half of the housing of the stage.

On Fig presents in isometric part of the rotor of the ORM (two steps) having a partition bifurcated with a groove. On one step and between the steps, local cutouts are made. Sections are not shaded.

Fig. 33 is an isometric collapsible spacer with an axis for SSE.

On Fig presents in isometric version of the SSE.

Fig. 35 is an isometric view of the ORM rotor stage with a separator and another SSE variant.

Description of the best sample.

To facilitate the description, we introduce the following definitions.

A sphere-shaped surface is understood to mean a surface resembling a sphere or part of a sphere, allowing small deviations from the ideal sphere, associated with manufacturing inaccuracies, the need to provide working clearances, and making seals, clearances to reduce viscous friction, etc.

By a sphere-shaped cavity is meant a cavity in which at least one of its limiting surfaces is a sphere-shaped surface.

The spherical part is understood to mean a part of the part that resembles a ball or part of a ball, allowing small deviations from the ideal shape of the ball due to manufacturing inaccuracies, the need to provide working clearances, to make seals, clearances to reduce viscous friction, etc. Channels will be called passages of various shapes for the working fluid, made inside or on the surface of the part, for example, holes, grooves, poles, obtained by casting or in another way, inside which the working bodies do not move (unlike working cavities, chambers), through which the flow of the working fluid constituting the supply of ORM (in contrast to the small branches of the working fluid for auxiliary needs, for example, unloading the working bodies or collecting leaks).

By the passage of the working fluid will be called the flow of the working fluid, which constitutes the supply of ORM (in contrast to the small taps of the working fluid for auxiliary needs, for example, unloading the working bodies or collecting leaks).

By interaction we mean both the force interaction, in which two parts work as a friction pair, and the sealing interaction between the two parts, in which they have the possibility of relative motion, but there are no leakages of the working fluid through the gap between them (if there is a gap) or are within the permissible limits for this device due to the small gap or due to the location of the elements in it.

Identical numbers in the description indicate elements of similar functionality.

The volumetric rotary machine (ORM) of FIG. 1 can be used as a pump and / or hydraulic motor. It is made in a submersible multi-stage version; w consists of several (in this example, four) steps 1, 2, 3, 4 pressed into the pipe 5 and tightened by nuts 6 in it.

Case 7 ORM, for the possibility of assembly, is divided into several parts. It consists of two extreme parts 8, three middle parts 9, four spacers Ιϋ.

The ORM rotor 11 is made common for several stages 1, 2, 3, 4 to balance the radial loads from them; For the possibility of assembly, the rotor 11 is made type-setting and contains a common shaft 12 having a part of the geometry of the steps, two extreme rings 13, three middle rings 14, four partitions 15, two output half-axles 16.

The rotor And is mounted to rotate around its axis 17 relative to the housing 7.

In each stage 1, 2, 3, 4, for cutting off the volumes, there is one separator 18 mounted for rotation relative to the housing 7. The axis 19 of rotation of the separator 18 is directed at an angle to the axis of rotation of the rotor 11. In this example, the angle is 25 degrees. The rotation of the separator 18 is associated with the rotation of the rotor 1L To improve the interaction conditions of the separator 18 with the rotor 11, they interact through a power synchronizing element (SSE) 20.

The ORM case 7 has the form of a cylinder 21 with a through hole coaxial to it 22. Along the cylinder 21, it has four (according to the number of steps) sphere-shaped cavities 23 with centers on the axis 17 of the hole 22, which is also the axis of rotation of the rotor 11. In each of the cavity 23, a circular groove 24 symmetrically passes along its surface 24. The plane of the groove 24 extends at an angle to the axis of rotation of the rotor 11. In this example, the groove 24 touches two opposite cylindrical sections 25 of the surface of the hole 22 separating (surrounding) the cavity 23. The axis of rotation 26 image boiling groove 24 is directed at an angle to the axis 17. In this example the angle is 25 degrees. The groove profile 24 is rectangular. The bottom 27 of the groove 24 is cylindrical, the side walls (ends) 28 - have the form of flat rings. The groove planes 24 in all cavities 23, in this example, are parallel. Near the surface of the cylinder 21 along the axis 17, two through pin holes 29 are symmetrically made. They are located at the maximum deflection of the grooves 24 along the axis 17, because there the distance from the groove 24 to the surface of the cylinder 21 is maximum.

The division of the housing 7 into the extreme parts 8, the middle parts 9 and the spacers 10 is obtained if you mentally dissect it with planes coinciding with the side walls 28. From the two ends of the cylinder 21 you get two extreme parts 8, between the planes coinciding with the side walls 28 of each groove 24 , spacers 10 are obtained, and the middle parts remain between them 9. One of the manufacturing options also involves the implementation of a solid cylindrical body 7, with a hole 21, cavities 22, and pin holes 29, then cutting it into the specified parts 8, 9, 10 thin wire on an EDM machine. Then increase the holes in the spacers 10 to form a groove 24. The original length of the housing 7 is restored by spraying a hard alloy on the cutting plane of parts 8 and 9 with their subsequent grinding. The pin holes 29 can also be made with a sharp wire, and they can be opened to the side surface of the cylinder 21 for the wire to enter.

The extreme part 8 of the housing 7 is obtained in the form of a cylinder with a coaxial through hole 22 and a sphere-shaped cavity 23, cut off by a plane inclined to the axis 17 of the hole 22, forming its flat inclined face 30 and passing through the cavity 23. The center of the cavity 23 is located on the axis 17 outside the extreme part 8. Section 25 of the surface of the hole 22 is located on the opposite side from the edge 30 of the cavity 23. Near the surface of the cylinder there are pin holes 29 extending along its axis 17, in places of its maximum and minimum lengths.

The middle part 9 of the housing 7 is obtained in the form of a cylinder with a coaxial through hole 22 and two sphere-shaped cavities 23, cut off from opposite sides by two parallel planes inclined to the axis 17 of the hole 22, forming its two flat inclined faces 31. The centers of the cavities 23 are located on the axis 17 behind the limits of part 9. Between the cavities 23 there is a portion 25 of the surface of the hole 22. Near the surface of the cylinder there are two symmetrical pin holes 29 running along the axis 17, in places of its maximum deviation along the axis 17.

The spacer 10 is obtained in the form of an oblique cut of the cylinder with a symmetrical cylindrical hole 32 and flat cut faces 33. Near the surface of the cylinder, there are two symmetrical pin holes 29 extending along its axis 17 at its maximum deflection along axis 17.

There are four stages 1, 2, 3, 4 on the rotor 11. Cylindrical sections 34 separate them from each other. Each stage 1, 2, 3, 4 of the rotor 11 has a central spherical part 35, the center of which lies on the axis 17, on both sides from it (along the axis 17) there are side walls 36, the surface of which has the form of a truncated cone of the coaxial axis 17. The geometric vertices of the cones are turned to each other and are at a distance from each other. The large bases of the truncated cones of the side walls 36 are joined with the sections 34 of the rotor 11. Between the side walls 36, an annular cavity 37 is opened outward, the bottom of which is a spherical part 35. In one place, the cavity 37 is partitioned across the partition 15 protruding from the spherical part 35. Thus, from the annular cavity 37, an open cavity 37 is obtained. The partition 15 has a spherical lateral surface 38, concentric with the spherical part 35, which fits into sections 34. The ends 39 of the partition 15 are flat. At the junctions of the partition 15 with the side walls 36, on the side walls 36 there is a recess 40 for entering a small part of the SSE 20. The surface of the recesses 40, located on both sides of the partition 15, is the surface of one cylinder, the axis of which is parallel to the generatrix of the side wall 36, lies in the plane of the partition 15 outside the side wall 36 and is directed to the center of the cavity 23. The partition of adjacent steps is deployed relative to each other by half a revolution around axis 17.

Inside the rotor 11, through all stages, two straight channels 41 are made for the passage of the working fluid. Their sections are in the form of a part of a circle (slightly less than half) with a cut off chord. Its corners are rounded. At the beginning of channel 41, between all steps 1, 2, 3, 4 and wider than the channel 41, the channels are alternately blocked by plugs 42. That is, in one channel 41, a plug 42 is installed in front of the first stage 1, in the second - in front of the second stage "2, etc. After the last stage in the next channel 41, a plug 42 is also installed. Partitions 15 are located along the interface of the channels 41, parallel to the wall 43 separating the channels 41.

On one side of the partition 15, on the surface of the spherical part 35, there is an entry window 44 for the working fluid leading to the channel 41, not blocked by a plug 42 in front of this stage. Window 44 is similar to an isosceles trapezoid with rounded corners (on a sphere), oriented with a large base to the partition 15 and adjacent to it. On the other side of the partition 15 through the surface of the spherical part 35 there is an exit window 45 leading to another channel 41, blocked by a plug 42 at the entrance to this stage. Since each next stage of the rotor 11 is rotated relative to the previous stage around the axis 17 by half a revolution, one channel 41 connects the exit window 45 of one stage with the entrance window 44 of the next stage. In the wall 43 there is an opening 46, the axis of which passes through the center of the spherical part 35 perpendicular to the wall 43. The hole 46 is used for fastening the SSE 20.

At the ends of the rotor 11 for communication with the drive and subsequent sections of the ORM, there are output half shafts 16, smaller in diameter than the diameter of the sections 34,

For manufacturability and for the possibility of assembling ORM with the described division into parts of the housing 7, the rotor 11 is divided into several parts.

The common shaft 12 of the rotor 11 is made in the form of a cylinder 47, on which there is a part of the geometry of steps 1, 2, 3, 4. Each stage 1, 2, 3, 4 is surrounded and separated by steps 1, 2, 3, 4 from each other sections 48 the surface of the cylinder 47. The geometry of the step on the shaft 12 consists of a central spherical part 35, and small parts of the side walls 36. To be able to put on the shaft 12 during assembly, an integral divider 18 with maximum tight contact on the spherical part 35 and the parts of the rotor 11, (overall) the cylinder diameter 47 is slightly (-0.1%) less than the diameter of the spherical portion 35. Moreover, on the spherical part, a slight decrease of 49 is obtained near its "equator". From the ends 50 of the cylinder 47 there are blind cylindrical holes 51, in which from the end 5Q a bore 52 is made of a slightly larger diameter with a thread 53 cut into it for installing the output half shafts 16. The channels 41 described above pass along the axis 17 of the shaft 12. They have outputs to the bottom holes 51. For the installation of the partition 15, at each stage of the shaft 12, a groove 54 is made along the axis 17. The depth of the groove 54 is such that it cuts the junction of the surface of the spherical part 35 with the side wall 36. The length along the axis 17 of the groove 54 is such that it slightly does not reach the side walls 36 of the adjacent steps, passing through part of the surface of the sections 48. The profile of the groove 54 is rectangular. The width of the groove 54 is approximately equal to the thickness of the wall 43. For connection of the "protrusion into the groove" type with the partition 15, symmetrically, at the bottom of the groove 54 there is a longitudinal rectangular groove 55 of a smaller size. Its width and depth is about 1/3 of the width of the groove 54. At the entrance of the groove 54 to the side wall 36 there is a cylindrical recess 40, the axis of which is parallel to the forming side surface 36, lies in the plane of the groove outside the side wall 36 and is directed to the center of the cavity 23.

In sections 48, circular grooves 56 are made for expandable retaining rings 57.

The middle ring 14 is made in the form of a cylinder with a through hole coaxially cylindrical hole 58. Its lateral surface is a cylindrical section 34. That is, one of the sections 34 of the rotor 11 is physically located on the middle ring 14. The ends of the middle ring 14 are parts of the side walls 36, i.e. surface of a truncated cone. In two centrally symmetric places of the middle ring 14 on its opposite walls 36 there are grooves 54 under the partitions 15, passing the ring 14 through the radius. At the entrance of the groove 54 to the side wall 36 there is a cylindrical recess 40, the axis of which is parallel to the generatrix of the side surface 36, lies in the plane of the groove outside the side wall 36. In the hole 58, a circular groove 56 is made for expandable retaining rings 57.

The extreme ring 13 is made in the form of a cylinder with a through coaxial cylindrical hole 58. Its lateral surface is a cylindrical section 34. That is, one of the sections 34 of the rotor 11 is physically located on the extreme ring 13. One end face 59 of the extreme ring 13 is flat. Another end of the outer ring 13 is a part of the side wall 36 of the extreme stage 1 or 4, i.e. surface of a truncated cone. In one place of the middle ring 14 on its wall 36 there is a groove 54 under the partition 15, passing the ring 13 through the radius. At the entrance of the groove 54 to the side wall 36 there is a cylindrical recess 40, the axis of which is parallel to the generatrix of the side surface 36, lies in the plane of the groove outside the side wall 36. In the hole 58, a circular groove 56 is made for expandable retaining rings 57.

The partition 15 is made in the form of a flat plate. Its section can be represented as the sum of the figures located symmetrically relative to each other: a long rectangle docked to its long side with its long side, a shorter rectangle and a smaller part of the circle cut off by a chord, which lies on the opposite side of the shorter rectangle. The plate thickness approximately coincides with the wall thickness 43. The flat ends are bound by the thickness of the plate 39. The free side of the long rectangle is bounded by a flat face 61. Its length is less than the length of the groove 54. It has a protrusion 62, corresponding to the groove 55. The sides of the large rectangle are perpendicular to it faces 63. The angles between the faces 63 and the ends 39 are rounded. The parts of the second long side of the long rectangle free from the short rectangle are bounded by convex cylindrical surfaces 64, the diameter of which corresponds to the diameter of the shaft 12, and the axis is parallel to this side and lies in the plane of symmetry of the plate. The sides of the short rectangle perpendicular to the long side are bounded by flat faces 65. The angles between the faces 65 and the ends 39 are rounded. The chord-free sections of the long side of the short rectangle are bounded by convex cylindrical surfaces 66, the diameter of which corresponds to the diameter of the rings 13, 14, coaxial with the surfaces 64. In a circular arc, the plate is defined by a sphere-shaped surface 38, coaxial with the surfaces 64, 66.

The output half shaft 16 is made in the form of three cylinders of different diameters. Larger and smaller cylinders are extreme. On the cylinder of larger diameter, a thread 68 is made mating to the thread 53, and at its end there is a blind central hole 69 from which several holes 70 extend radially axially outwards through the end of the middle cylinder. Holes 69, 70 serve to pass the working fluid from channel 41 outside rotor 11. On the cylinder of a smaller diameter, flats (splines) 71 are made for coupling by torque with an external drive or load.

The separator 18 is made in the form of a flat disk with a cylindrical lateral surface 72 and flat ends 73. The axis 74 is the axis of rotation of its generatrix. A through hole 75 is made in its center. The surface of the hole 75 is spherical. Its diameter is close to the diameter of the spherical portion 35 for possible interaction between them. The thickness of the separator 18 corresponds to the width of the groove 24. From the center of the hole 75, along its radius, parallel to the ends 73, a separator 18 has a cylindrical hole 76 with a diameter slightly exceeding the thickness of the separator 18. The bottom 77 of the hole 76 is sphere-like for convenience, and the diameter coincides with the diameter of the hole 76. The hole 76 forms on the separator 18 a through slot 78 open to the hole 75 and to the ends 73. The hole 76 is extended by a coaxial through hole 79 thereof smaller than the thickness of the diameter divider 18. With the slot 78, the separator 18 is put on during assembly on the partition 15, and the SSE 20 is partially located in the holes 76.79. Moreover, the partition 15 enters the slot 78 and, when it is rotated about the axis 80 of the holes 76, 79, an angle equal to the angle between the axis 17 and the axis 26 .

When assembling, the outer (more distant from the center of the separator 18) part 81 of the separator 18 is located in the groove 24, and the inner (closest to the center) part 82 protrudes into the cavity 23. In figure 12, the outer part 81 is separated by a dashed line from the inner part 82 . The hole 76 passes through the entire inner part 82, and slightly goes into the outer part 81.

SSE 20 (Fig.13) is made in the form of a cylinder 83, in which one end 84 is sphere-shaped. The diameter of the cylinder spindle 83 and the end 84 corresponds to the diameter of the hole 76 in the separator 18. The length of the cylinder 83 is slightly greater than the radius of the cavity 23. The cylinder 83 is dissected from its other end 85 by a symmetrical through flat groove 86 under the partition 15 extending along the axis 87 of the cylinder 83. The bottom 88 of the groove 86 concave sphere-shaped. Its diameter corresponds to the diameter of the cavity 23 (or surface 38), the center lies on the axis 87 of the cylinder 83. From the end 84, a cylindrical axis 89, coaxial to the cylinder 83, whose diameter corresponds to the diameter of the hole 79. Closer to the end face 85, through the center of the sphere-shaped bottom surface 88, perpendicular to the plane of the groove 86, coaxial through holes 90 and 91 are made. The hole 90 passes through the cylinder 83 to the groove 86, and the hole 91 passes the cylinder 83 behind the groove 86. The diameter of the hole 90 is slightly larger and there is a thread in the hole 91. At the end 84, there are two small cylindrical notches 92. Each of them has a cylindrical platform 93, coaxial to the axis 87, with an angular length equal to the double angle between the axis 17 and axis 26, and the flat faces 94 extending its tangents extending to it. The diameter of the area 93 coincides with the width of the groove 24. The bottom of the notch 92 is convex, and in position and diameter coincides with the bottom 88. The middle of the notches 92 lie in the plane of the groove 86.

An ORM is being assembled, for example (not optimal, but the most understandable assembly procedure has been selected), as follows. The output half-shafts 16 are screwed into the holes 51 of the shaft 12. A spacer retaining ring 57 is installed in the groove 56 located on the extreme portion 48 of the extreme stage 1 of the shaft 12, after which the extreme ring 13 is put on (tapped). When the extreme ring 13, the retaining ring 57 is expanded and, falling on the boundary of the grooves 56 of the shaft 12 and the extreme ring 13, fixes the extreme ring 13 on the shaft 12. Wears on the extreme ring 13 the outermost part 8 of the housing 7. On the shaft 12, the spacer 18 is put on with the hole 75 and moves to the position on the spherical part 35 of the stage 1 at an angle to the axis 17, pressing the end face 73 against the edge 30 of the outermost part 8. The extreme part 8 and the spacer 18 are oriented so that the slot 78 is directed toward the extreme part 8 and along the groove 54. With the groove 86, the SSE 20 is put on the wall 43. Then it is inserted into the hole 76 of the separator 18. A partition 15 is inserted into the groove 54 of the stage 1. By moving along the groove 54, it starts in groove 86 of SSE 20 and in groove 54 of extreme ring 13. SSE 20 fasten relative to the center of the spherical part 35 with a bolt 95 through holes 90, 91 and 46 to the wall 43. Thus, in addition to fastening with the help of the axis 89 in the spacer 18, in this design the SSE 20 can be fastened to the rotor 11 using the second the physical axis — bolt 95. On the next section 48 of the shaft 12, an expandable retaining ring 57 is installed and the middle ring 14 is put on so that it slots on the partition 15 with the groove 54. The middle ring 14 presses the surface 64 of the partition 15 from its radial diameter displacement. From axial movement, the partition 15 is fixed by clamping between the grooves 54 of the middle ring 14 and the extreme ring 13 along the faces 65. The spacer 10 is put on. The pins 96 are inserted into the holes 29, fixing the spacer 10 to the end part 8. The shaft 12 is rotated half a turn. The middle part 9 of the housing 7 is put on the shaft 12 and the pins 96. The separator 18 is put on the stage 2, and the process is repeated until all stages 1, 2, 3, 4 of the rotor H and the housing 7 are assembled. The assembled rotor 11 and the housing 7 are pressed into the pipe 5. Thrust bearings 97 are installed on the output half-shaft 16 and the entire assembly in the pipe 5 is tightened on both sides by nuts 6.

The machine of figure 1 works as follows. In the assembled state of the ORM, in the cavity 23, around each spherical part 35, an annular working cavity 37 is formed between the side walls 36. The separator 18, installed at an angle in the cavity 37, interacts with the hole 75 with the spherical part 35, and each end 73 interacts with the side wall 36, twice blocking the cavity 37 with its inner part 82. In one place 98, he blocks the cavity 37 with its c-shaped part (half) on which there is no slot 78 creating an obstacle for the working fluid. In another place 99, he blocks the cavity 37 with another c-shaped part (half), on which there is a slot 78, without creating an obstacle for the working fluid, since the slot 78 all the time follows the partition 15, on one side of which the entry window 44 is made, and on the other hand, the exit window 45 of the working fluid, and the working fluid can pass through them from one side of this c-shaped part of the separator 18 to the other side. Due to the rotation of the separator 18, the places 98 and 99 change all the time with respect to the housing 7. There is a point in time (a small part of the OPM cycle) when the slot 78 of the separator 18 passes the place of its interaction with the side wall 36. At this moment, the separator 18 is cut by 78 is shifted to the edge of the partition 15 and the windows of the entrance 44 and / or exit 45 are completely on one side of the separator 15. With one of the side walls 36, the separator 18 at this moment interacts through the SSE 20. At this moment, the separator 18 may, depending on the details execution of windows 44 and 45, in one and and at two locations of the cavity 37 to create an obstacle to the working fluid, and on one side of the separator 18 can not be closed variable volume. In the cavity 37, due to rotation together with the rotor 11, the partition 15 moves. It is always located in the slot 78 of the separator 18 and also blocks the cavity 37. Thus, the cavity 37 is blocked for the working fluid in one or two places motionless relative to the housing 7 the barrier - the separator 18 (the rotation of the separator 18 does not displace its plane relative to the housing 7), while in another place it is blocked by a moving partition 15. Therefore, before the partition 15 (in the direction of rotation of the rotor 11) a decreasing in size camera 100, and behind the partition 15 an increasing chamber 101 is formed. The working fluid enters the chamber 101 through the entrance window 44 located behind the partition 1 from the supply channel 41, and leaves the chamber 100 through the exit window 45, located in front of the partition 15, into the discharge channel 41. SSE 20, most of the time, does not participate in cutting off the working chambers 100, 101, it only matches the rotation of the separator 18 with the rotation of the rotor 11. But for a short time, when the partition 15 passes through the line of interaction of the end face 73 of the separator 18 with the side wall 36, and this interaction line goes directly to SSE 20, SSE 20 also participates in the separation of chambers 100 and 101. Since the fraction of this time relative to the ORM cycle is small, and the speed of SSE 20 relative to the partition 15 and separator 18 is very small at this moment, this moment practically does not affect either the wear of the SSE 20, or internal flows. However, the presence of a short pulsed load should be taken into account when choosing the SSE 20 material, and the safety factor of its axis 89.

This design has the following positive aspects. ORM is quite compact, because the length of one step is small and is about half the diameter of the cavity 23, and the diameter of the ORM is mainly determined by the diameter of the groove 24, i.e. no space is occupied for the passage of the working fluid around the groove 24. The supply of ORM is almost uniform. The inner part 82 of the separator 18 is subject to variable periodic sawtooth axial load from the side of the working fluid, which is transmitted to the outer part 81 and then to the side walls 28 of the groove 24. Due to the variability of the load and the rotation speed of the outer part 81 of the separator 18, during negative load, into the gaps between the ends 73 of the separator 18 and the side the walls 28 of the groove 24 under pressure, the working fluid enters and serves there as a lubricant and support for the separator 18 at a time when the load is positive. A similar variable periodic sawtooth radial load acts on the surface of the hole 75, which is transmitted through the side surface 72 to the bottom 27 of the groove 24. The area of the side surface 72 is larger than the surface area of the hole 75, which weakens the specific load. Due to the variability of the load, and the rotation speed of the outer part 81 of the separator 18, during a negative load, the working fluid under pressure enters the gaps between the side surface 72 of the separator and the bottom 27 of the groove 24 and serves there as a lubricant and support for the separator at a time when the load is positive. The specific load on the friction pairs in these places is maintained within acceptable limits due to the sufficient support area and due to the conditions for the emergence of a hydraulic layer between the friction pairs. On the front wall of the hole 76 of the separator 18, located in the high pressure zone, there is a force from the side of the working fluid creating a torque that contributes to the rotation of the separator 18 and compensates for the effect of friction forces. This moment is greater, the greater the thickness of the inner part 82 of the separator 18. On the SSE 20 practically no forces from the working fluid, because he practically does not take part in the separation of volumes with low and high pressure of the working fluid. One part of it is almost always located in the high pressure zone (in front of the partition 15) and the second in the low pressure zone (behind the partition 15). The area connecting the jumper parts (between end 84 and bottom 88) is small. An exception is the point in time when the contact line of the end face 73 of the separator 18 with the side wall 36 passes directly along the SSE 20. The SSE 20 carries a load by coordinating the rotation of the rotor 1.1 with the separator 18. The partition 15 transfers force to the side surface of the groove 86 of the SSE 20, and it transfers it through the surface of the cylinder 83 to the surface of the hole 76 of the separator 18. Most of the time this force is not large, because is the difference between the friction moment of the separator 18 in the groove 24 and the described torque from the side of the working fluid. But when starting an ORM under pressure or when operating at low speeds, or when starting after a long break and the associated deposition of salts, the load transmitted through this friction pair can be on the order of 10% of the power of the stage. Pressed by the described load to the partition 15, SSE 20 should move along it, rotating relative to the bolt 95, tracking the change in the slope of the spacer 18 with the hole 76. This movement occurs due to the interaction between the cylinder 83 and the surface of the hole 76 (not always reliable due to the small angles), and, reliably, due to the force interactions between the axis 89 of the SSE 20 and the bore 79 of the separator 18. The load is reduced by the fact that this force has a shoulder approximately 2 times larger than the friction force that impedes movement. The shoulder is created by attaching the opposite ends of the SSE 20 with the help of the axis 89 in the spacer 18 and with the help of the second physical axis - the bolt 95, in the center of the spherical part 35, to the wall 43 of the rotor 11. The friction force, however, acts approximately on the middle of the SSE 20 The friction force itself is about 10% (friction coefficient) of the interaction force of SSE 20 with separator 18 (partition 15). In other analogs known to the author, on the contrary, the shoulder of the friction force exceeds ~ 2 times the shoulder of the force holding the SSE or SSE, making the SSE or SSE the weakest element determining the resource and reliability of the ORM.

The rotor 11 is almost balanced in radial loads, because loads of steps 1, 2, 3, 4 balance each other. Since the distance between the steps is small, the moment of forces from the radial loads of different steps is small. The axial load of the rotor 11 is transmitted to the thrust bearings 97.

For hydraulic unloading of the rotor 11 (Fig. 15), all or part of the middle rings 14 and the outer rings 13 is divided into two parts. From the middle rings 14, exactly the same one-sided rings 102 are obtained as the slightly shortened end rings 13. From the extreme ring 13, a one-sided ring 102 and a flat ring 103 are obtained. Between them, with end gaps, housing parts 7 are arranged in the form of rings 104. Their outer the diameter is (for tight installation or pressing) the diameter of the hole 22, and the diameter of the hole 58 is close (for interaction) to the diameter of the portion 48. On the outer cylindrical surface 105 a circular groove 56 is made for the retaining ring 57. The corresponding grooves 56 perform and in the openings 22 of the housing 7. In sections 48, another groove 56 is added to fix the one-sided rings 102. When assembling, the ring 104 is located approximately in the middle of the section 48. On both sides of this place, holes 106 are made leading to the channel 41. At this point (between the previous stage 1/2/3 and the next stage 2/3/4), in the channels 41 there are three different pressures: the inlet pressure of the previous stage, the outlet pressure of the previous stage being the inlet pressure of the next stage, and the outlet pressure of the next stage. For unloading, you can use any two different pressures. Depending on the required pressure, the holes 106 go either to the channel 41 with a plug 42 in this place, and pass it at an angle in the desired direction or go into the channel 41 without a plug 42 in this place. In this example, holes 106 are made that exit to the channel 41, in which there is no plug 42, and holes 106 that exit to the channel 41, which come out after the plug 42. In this way, the axial discharge of the rotor 11 is completely possible. differs from the above. Instead of one middle ring 14 (extreme ring 13), a one-way ring 102, a ring 104 and another one-way ring 102 are installed.

For hydrostatic unloading of the separator 18 (Fig. 16) from axial forces, grooves 107 are made on the side walls 28 of the groove 24 in the form of closed loops along the perimeter of the site. Long circuits may have shunts. Two or more grooves 107 per each side wall 28. Moreover, in the region of the maximum deviation of the groove 24 along the axis 17, there is an interface between the grooves 107. And on the separator 18 (Fig.17), near the interface between the inner and outer parts 82, 81, there are made circular holes 108 leading from one side of the inner part 82 to the other side of the outer part 81, passing the separator 18 at an angle to the axis 74 The outputs of the holes 108 fall into the grooves 107. Another possibility (Fig) is the placement of many small contours of the grooves 107 at the ends 73 of the outer part 81 of the spacer 18, each of which extends at least one hole 108. Holes 108 that extend beyond grooves 107, go to the inside of 82 ra the separator 18 of the grooves 107 located on its invisible side on the outer part 81. That is, holes 108 are made at an angle to the axis 74.

Such unloading of the separator 18 operates at any speed of rotation of the rotor 11 and almost completely remove the load from the friction pairs of the separator 18 - groove 24. The price for this may be an increase in the internal flows of the working fluid. The efficiency of ORM, due to unloading, can either increase or decrease depending on the size of the working clearances and the properties of the working fluid.

To increase the strength of the SSE 20 (Fig. 19), and to increase the reliability of the ORM, the axis 89 of the SSE 20 can be increased in diameter to the diameter of the cylinder 83. That is, SSE 20 is obtained similar to SSE 20 of FIG. 13, but simplified, in the form of a cylinder 83, cut from one end 85 by a groove 86, the bottom 88 of which is spherical. Near the end face 85 through the SSE 20, perpendicular to the plane of the groove 86, for fastening the SSE 20 to the rotor 11, a hole 90 passes into the threaded hole 91 when the groove 86 passes. In this case, the outer part 81 of the spacer 18 (FIG. 20) is made thicker than the inner part 82. The easiest way is to make the end face 109 of the inner parts 82 are conical. Then the hole 76 becomes through (the hole 79 with the bottom 77 just disappears) and more technological, and when assembling the SSE 20 is installed: in the separator 18 from the outside. To pass the partition 15 at different angles, at the entrance of the hole 76 to the outer part 81, a sphere-shaped bottom 110 is made around it, and on the inner part 82, bevels 111 are made between the ends 109 and the cylindrical surface of the hole 76. Since the separator 18 is partially dissected by a slot 78 and weakened by hole 76 in only one place, it remains strong and rigid enough. Thus, the SSE 20 receives a very reliable fastening in the tire part 81 of the separator 18 located there over its entire width (radius) of a solid cylinder 83 of sufficient diameter and securely fastened with a bolt 95 (or an axle, a pin or another way) to the rotor 11, because in the channels 41 of the spherical part 35, there is also enough space to accommodate a reliable fastening. Those. SSE 20 in this design is not a weak link and does not determine the resource and reliability of ORM. The disadvantage compared to the embodiment of FIG. 1 is the complication of preparation т by introducing the end face 109, which interacts with the side wall 36, in comparison with w (we joke when the inner and outer parts 82, 81 have a common flat end 73.

In the above embodiments, the side walls 36 are made on the rotor 11, and the interaction between them and the ends 73 of the separator 18 occurs along the line. Hosht length and not great (unlike screw pumps), but under certain conditions, zsh sheshivaetsya on the magnitude of the internal flows. With the side walls 36 on sspnyce 7 (Fig. 21), it becomes possible to turn this interaction into a better densified area interaction. For this purpose, on one-sided rings 102, before their fastening to the body 7, the grooves 56 are made not in the hole 58, but in section 34. In the box 104, for its fastening to the shaft 12, the grooves 56 are made in the hole 58. Moreover, on Yezhov the walls 36 of the one-sided rings 102 (Fig. 22), at the place of their interaction with the ends 73 of the separator 18, a shallow (about 0.1% of the cavity diameter ^) almost tangent incision 113 is made, corresponding to the shape of the surface of the ends 73. In the ebar, the superficiality 36 on one-sided rings 102 to the depth of the notch 113 will act as a part of the surface 36 remaining on the shaft 12. The grooves 54 on the one-sided rings 102, when they are attached to the housing 7 are not performed. Since the notch 113 can be located in the place of interaction with the separator 18 (the place where the groove 24 touches the surface of the holes 22), in order to maintain the orientation of the one-sided ring 102 along the axially 17 axis, it may be necessary to additionally attach it to the body 7 with pins, screws or other known method ( not shown). Removers 45 fastens only in the groove 54 of the shaft 12. Therefore, that part of its shape that is associated with the mount changes. The partition 15 (Fig.23) is made in the form of a flat plate. The cross section can be approximately represented as the sum of the figures located symmetrically relative to each other: a long rectangle and a truncated sector of the circle docked to its long side. The thickness of the plate approximately coincides with the thickness of the wall 43. The flat ends are bound by the thickness of the plate 39. The free side of the long rectangle is bounded by a flat face 61. Its length is less than the length of the groove 54. It has a protrusion 62, a prominent groove 55. The sides of the rectangle perpendicular to it are bounded by flat faces 63. The angles between the faces 63 and the ends 39 are rounded. Free from the sector of the circle, parts of the second long side of the rectangle are limited by convex cylindrical surfaces 64, the diameter of which corresponds to the diameter of the shaft 12, and the axis is parallel to this side and lies in the juiciness of the symmetry of the plate. The sides connecting the rectangle with the arc are bounded by Concave conical faces 114. A sphere-shaped surface 38, coaxial to surfaces 64, 66 delimits the plate along the arc.

The location of the walls 36 on the housing 7 reduces the axial load of the rotor 11, also. reduce its diameter subject to pressure of the working fluid. Therefore, the relevance of unloading the rotor 11 with the help of rings 104 is reduced. If the unloading is not performed, 1 six-sided rings 102 and rings 104, the middle rings 14 and the extreme rings 13 are attached, which are attached to the housing 7 by transferring grooves 56 to their sections 34 pieces in any other way. The notches 113 are filled in the same way, on their surface ^ (x shown). The disadvantage compared with the location of the side walls 36 on the rotor is the weakening of the fastening of the baffle 15. To strengthen it, the baffle 15 can additionally be attached to the shaft 12 by welding "

There is a compromise option (Fig. 24) of the location of the stand 36, which allows less weakening of the partition 15 and obtain a more economical full hydraulic unloading of the rotor 11. In it, the middle rings 14 are made of two one-sided rings 102, one of which is attached to the housing 7 (as it was readings "Fig. 21), and another one-sided ring 102, is attached to the shaft 12 (as shown fsh-.15). At the same time, a low pressure is supplied into the gap between two adjacent one-sided rings 102 from the pass from the channels 41 through the openings 106 if the unilateral ring 102 fixed to the shaft 12 is located on the high pressure side (outlet <E £ M operating as a pump) or high pressure otherwise. For the same strength of the partitions 15 different steps, it is better to have at least one wall 36 made on the rotor 11 in each step. Such unloading may be redundant for the rotor 11. In this case, the side walls 36 are different in arrangement on the rotor 11 (on the housing 7 or on the rotor 11) stage. Obviously, the extreme rings 13 can also be divided into one-sided rings 102 and rings 303, some of which are attached to the housing 7, and others to the shaft 42.

Since on one side of the partition 18 (Fig. 25), in this embodiment, a one-sided ring 102 with a groove 54 fixed relative to the rotor 11 is located, and on the other side of it there is a one-sided ring 102 stationary relative to the housing 7, then, accordingly, one part of the partition 15 is executed as a half of the non-partition of FIG. 10, and the second part of the partition 15 is executed as a half of the partition of FIG. 23. Therefore, the partition 15 is obtained in the form of a plate, which is limited by the thickness of the flat ends 39. On the one hand, it is bounded by a flat face 61. Its length is less than the length of the groove 54. It has a protrusion 62, the corresponding groove 55, its perpendicular sides are bounded by flat faces 63. The angles between the faces 63 and the ends 39 are rounded. They are adjacent to the convex cylindrical surface 64, the diameter of which corresponds to the diameter of the shaft 12, and the axis is parallel to the face 61 and lying on the plane of symmetry of the plate. To them, on one side of the plate, is adjacent a plane face 65 parallel to face 63. The angles between faces 65 and ends 39 are rounded. On the other hand, a concave conical surface 114 adjoins. A sphere-shaped surface 38, coaxial to the surface 64, joins to the surface 114. The surface ЗВ w face 65 connects the coaxial surface 64 to the cylindrical surface 66, the diameter of the cord corresponds to the diameter of the rings 13, 14 or 102. A truncated circle sector is obtained, bounded on both sides by protrusions for mounting in a groove 54, bounded on a part of a third side by a similar protrusion. The partition 15 has a conical surface 114 for interaction with the side wall 36 and a sphere-shaped surface for interaction with the surface of the cavity 23.

The simplicity of unloading the rotor 11 is to reduce the internal flows of the working fluid due to the fact that the pressure is different from the pressure in the surrounding area in only one gap between two one-sided rings 1 # 2, SfjOTHB for supplying different pressures in two gaps formed between two food-side rings 102 and ring 104 in previous embodiments. In this ORM, you can use the separator 18 without SSE 20 or with other types of SSE 20. When using the separator 18 without SSE 20 (Fig.26), the side surfaces 115 of the slot 78 of the separator 18 are convex, cylindrical (or conical). The axis 116 of the surfaces 115 passes through the center of the sphere-shaped part 35. The axis 116 of the two surfaces 115 extend at an angle to each other. The bottom 110 of the slot 78 is sphere-shaped to interact with the partition 15.

The partition 15 in this embodiment is not flat. The part responsible for fixing in the groove 54 may remain the same as that of the partitions 15 of FIG. 10, 23 or 25, depending on the location of the side walls 36, but on the site, in the form of a truncated sector of the circle, end faces 39, to interact with the surfaces 115 of the separator J8, a profile surface 117- appears

The profile surfaces 1 17 of the partitions 15 are concave in the form of a part of the side surface of the cone, the geometric axis of which passes through the center of the spherical part 35, perpendicular to the axis 17 directed by the apex to the axis i. The top of the cone does not reach the axis 17. That is, axis 17 remains outside this cone. The distance r of the indirect direction directed along the generatrix of the cone to the center of the spherical part 35 is equal to the radius of the surface 115 of the separator 18. To be able to put the separator 18 with a slot 78 on the partition 15, the edges 118 (in the angular direction) of the profile surface 117 are cut off. To be able to fit into groove 54 during assembly, the faces: € 3 EE are clenched at an obtuse angle to the face 61. One corner 119 of the profile surface 117 is cut. To interact with the surface of the cavity 23, the partition 15 has a sphere-shaped surface 38, coaxial to the surfaces 64, 66.

The separator 18 interacts with the partition 15 to cut off the volume only at the time the contact line of its end 73 with the side wall 36 passes through the partition 15. The rest of the time between the separator 18 and the partition 15 there is a power contact to maintain the rotation of the separator 18 and synchronize it with the rotation of the rotor П . In a multi-stage ORM, you can not worry about the interaction of the separator 18 e partition 15 to cut off the volume. During the passage of this phase in one step, its contribution to the pressure difference of the ORM is distributed among the others, rotated relative to its steps. In this case, significant deterioration of the separator surface 115 can be allowed; ! &.

The separator 18 in the embodiment of FIG. 26 may be provided with an SSE 20 (FIG. 28) in the form of a lever 120 mounted at an angle on the axis 121. It is mounted inside the spherical part 35, on the axis 121, which is mounted in the holes 122 of the spherical part and / or in the opening 122 of the partition 43. The axis 121 of the SSE 20 passes through the center of the spherical part 35 almost at right angles to the plane of the partition 15. The lever 120 passes to the separator 18 through the exit window 45 (or through the entrance window 44). The lever 120 ends with an axis 124 in the form of a cylinder, which enters the hole 123 (shown in Fig. 26) of the spacer 18, made along axis 1 16. To be able to assemble the SSE 20 inside the spherical part 35 and insert the axis 124 during assembly into the hole 123, the lever is attached to the cylinder 125, with an opening for pressing on the axis 121. In the holes 122, the axis 121 is mounted in bearings 126, which are pressed into the holes 122. The axles 124 and 121 are angled to each other (closer to 90 degrees).

The breakdown of the ORM into parts may be different. When performing the partition 15, for strength integral with the rotor 11, the housing 7 must be divided into parts with a longitudinal plane. In this case, it is possible to fasten part or all of the side wall 36 to the rotor 11 or to the housing 7. The fastening of the side wall 36 to the housing 7 allows the splitter 18 to be made integral. In FIG. 30 shows an example of the implementation of the integral with the rotor 11 of the partition 15, collapsible along the axis 17 of the housing 7, and an example of the use of another type of SSE 20.

Multistage ORM is made in submersible version. It contains several (two figures are shown) cases of 127 steps, a rotor 11 common to several steps, made on one shaft 12, and one spacer 18 for each step. The housing 127 of the stage is made in the form of a cylinder 21 with a coaxial hole 22 for the passage of the shaft 12 of the rotor I. The housing 127 has a sphere-shaped cavity 23 centered on the axis of symmetry 17 of the cylinder 21 / hole 22. On the surface of the cavity 23, a circular groove 24 is made open into the cavity 23 The bottom 27 of the groove 24 is a sphere-shaped (for convenience of execution) surface of the concentric cavity 23. The lateral walls 28 of step 24 are flat. The axis 26 of rotation of the generatrix of the groove 24 is directed at an angle to the axis 17. In this example, the angle is 25 degrees. The groove 24 is flat and symmetrical. We can say that the plane of the groove 24 extends at an angle to the axis 17 which is the axis of rotation of the rotor 1 1, or shorter: the groove 24 is made at an angle to the axis of rotation 17 of the rotor 11. For assembly, the stage housing 127 consists of two mirror-symmetric parts. The plane of the connector 112 between them passes through the axis 17 perpendicular to the plane of the groove 24. That is, it contains the axis of rotation 26 of the generatrix groove 24. Dm alignment of the halves of the housing 127 during assembly, pin holes 128 are made in the corners of each half of the housing 127. A keyway can extend along the outside of the housing for additional fixation from rotation in the pipe 5. Between the housing 127 steps can be fitted with shims or threaded spacers.

The rotor 11 on one shaft 12 has several stages. 32 shows two stages 1 and 2. The sections 34 of the shaft 12 separate them from each other. Each stage of the rotor 11 has a central spherical part 35, the center of which lies on the axis 17, on both sides of it (along axis 17) walls 36, the surface of which is in the form of a truncated cone of the coaxial axis 17. The geometric vertices of the cones are turned to each other and are at a distance from each other. The large bases of the truncated cones of the side walls 36 are joined with the portions 34 of the shaft 12 of the rotor 11 on the transition surfaces 129. They are made sphere-shaped for the convenience of manufacturing the housings 127. The centers of both transition surfaces coincide with the center of the spherical part 35. Between the side walls 36, an annular cavity 37 open to the outside is obtained , DYOM which serves as a spherical part 35. In one place, the cavity 37 is partitioned off across the partition 15 protruding from the spherical part 35. Thus, it turns out from the annular cavity 37 I have a cavity 37. The partition 15 has a spherical lateral surface 38, coaxial with the spherical part 35, the diameter of which coincides with the diameter of the transition surfaces 129. That is, they are bounded by a common sphere-shaped surface. The ends 39 of the partition 15 are limited by a curved surface. The partition looks like a sector of a circle. She's a little thinner in the middle.

Along the partition 15, along its lateral surface 38, a guide groove 130 extends. In depth it approximately reaches the spherical part 35. The angular size slightly exceeds the angular size of the partition 15, i.e. its edges extend onto the transition surface 129. The side walls of the guide groove 130 are flat. The groove 130 serves to synchronize the rotation of the separator 18 with the rotor 1 1. Due to the separation of the partition 15 by the groove 130, we can talk about the presence of two partitions 15. By design, the partition 15 can be stacked, i.e. double, triple, etc.

Inside the shaft 12 of the rotor 11, through all stages, two straight channels 41 are made for the passage of the working fluid. Their sections are in the form of a part of a circle (slightly less than half) with a cut off chord. Its corners are rounded. At the beginning of the channel 41, between all the steps and at the end of the channel 41, the channels 41 are alternately blocked by plugs 42. That is, in one channel 41, a plug 42 is installed in front of the first stage 1, in the second - in front of the second stage 2, etc. After the last stage, a plug 42 is also installed in the next channel 41. Partitions 15 are located along the interface of the channels 41. On one side of the partition 15 (behind the partition along the rotation of the rotor 11), through the surface of the spherical part 35, the entrance window 44 of the working fluid is made. The window 44 is similar to an isosceles triangle with rounded corners (on a sphere), oriented by the smaller side to the partition 15. On the other side of the partition 15 through the surface of the spherical part 35, the exit window 45 of the working fluid is made.

Each next stage of the rotor 11 is rotated relative to the previous stage around the axis 17 by half a turn. Those. the partitions 15 of the adjacent steps 1, 2 of the rotor 11 are deployed in opposite directions.

To communicate with the drive or the load, an opening is made at the end of the shaft 12 of the rotor 11 into which the output half shaft 16 is pressed (not shown separately in the figures). The working fluid enters the channel 41 through the openings 70, 69 into the half shaft 16 at the beginning of the rotor 11. The working fluid exits through the same holes in the other half shaft 16 at the end of the rotor 11.

The separator 18 (Fig.ZZ) is made in the form of a flat disk with a sphere-shaped lateral surface 72 (for convenience of groove 24 on the housing 127) and flat ends 73. The axis 74 is the axis of rotation of its generatrix. A through hole 75 is made in its center. The surface of the hole 75 is spherical. Its diameter is close to the diameter of the spherical part 35 for the possibility of interaction between them. From the side of the hole 75, internal, i.e. the part 82 closest to the center of the hole 75 (the inner part 82 is limited by a dashed-dotted circle in the figure) of the spacer 18, is cut by a through slot 78. The bottom of the slot 78 is sphere-shaped. Its diameter is close to the diameter of the side surface 38 of the partition 15 for the possibility of interaction between them. A hole is made in the radial direction in the middle of the bottom of the slot 78 in the radial direction, into which the axis 131 is pressed. A power synchronizing element (SSE) 20 is put on the axis 131. The lateral surfaces 115 of the slot 78 are convex. In this example, a conical surface is made on them for interfacing with the ends 39 of the partition 15, for working on it as a friction pair in case of failure of the SSE 20 and to protect it from overload.

For the possibility of assembly, the separator 18 is made of two parts. The connector 135 between them is made by the type of "protrusion into the groove." The protrusion 133 is the smaller part, in the middle of which is the slot 78. The front edge of the protrusion 133 extends along the diameter of the hole 75. In the middle of the front edge of the protrusion 133 is the center of the hole 75. The groove 134 is made on the other part of the separator 18. The interface between them is directed along the axis 131. In addition, on the side walls of the protrusion 133, in the middle, small protrusions 132 are made along the plane of the separator 18, and a small response groove is made on the surface of the groove 134. For the mutual fastening of the parts of the separator 18 in the area of the connector 135 there is a hole for the pin 136.

SSE 20 (Fig. 34) is made in the form of a truncated sector of the circle. Its ends 137 are flat, parallel, the convex side face 138 is bounded by a sphere-shaped surface with a diameter close to the diameter of the bottom 110 of the slot 78. In parallel to the ends 137, symmetrical in radius, a through hole 139 is made under the axis 131. The thickness of the SSE 20 corresponds to the width of the guide groove 130 The length of the SSE 20 along the hole 139 is slightly less than the depth of the groove 130, so that there would be room for the passage of the working fluid from the volume pinched into the groove 1 0.

ORM is collected, for example, as follows. On the part of the separator 18 with a slot 78, an SSE 20 is installed on the axis 131. Next, these parts of the separator 18 are worn on the steps of the rotor 11, so that the SSE 20 falls into the groove 130, and the hole 75 of the separator 18 sits on the spherical part 35. After that, the connector 135 is installed the second part of the separator 18 and the connection is fixed by pressing the pins. On the steps of the rotor 11 with the installed dividers 18, halves of the housing 127 are assembled on the pins. The bearings (not shown) are mounted on the ends of the rotor 11, and this assembly is pressed into the pipe 5, in which it is tightened with nuts 6 on both sides.

When working with a high viscosity working fluid (Fig. 35), the forces on the SSE 20 are unilateral, therefore, to strengthen it, it does not work inside the groove 130, but directly at the end 39, which is made in place of the side wall of the groove 130 of Fig. 30. i.e. the partition 15 is made asymmetrically (not in the radial direction). The SSE 20 fastening is reinforced by the implementation on the end 137 of the cylindrical platform 140, the pine hole 139. On the side surface 110 of the slot 78 of the spacer 18, a mating cylindrical platform is made.

One stage ORM can be used independently.

On one shaft 12 can be performed, due to their small length, many stages of ORM. In this case, it is advisable to turn the next steps of the casing 7 or the steps of the rotor 1 1 around the axis 17 a little after 2 to 4 steps to separate the moments of passage of the area of interaction of the separator 18 with the side walls 36 of the partition 15 at different steps. For hydraulically parallel connection of several stages of ORM, between them in the channels 41 are not installed plugs 42.

For unloading from axial force, the output / input of the working fluid can be arranged in the middle of the ORM, through openings from one of the channels 41, and the inputs / outputs at the ends of the rotor. The ORM stages, however, can remain the same. The feed direction of the part of the steps is changed due to another (symmetrical) arrangement of the plugs 42.

In order for one step to be tight throughout the cycle, and without the exact execution of the lateral sides 110 of the slot 78, elastic seals can be installed on the surface of the side walls 36, near the partition 15.

To unload the separator 18 from the radial load, radial holes can be made in it, leading from the surface of the hole 75 to the side surface 72.

To reduce overflows through the gap between the surface of the hole 75 and the spherical part 35, an O-ring with a T-shaped or U-shaped profile can be installed on the inner part 82 of the spacer 18, onto which the sphere-shaped surface of the hole 75 is transferred. A hole of a larger diameter is made on the spacer 18, on the surface of which a circular groove is made or a protrusion is left to install a snivel ring. When using a sealing ring, the diameter of the spherical part is made equal to or slightly smaller than the diameter of the shaft 12, and exposure 49 is not performed.

Instead of fastening in the housing 7 or on the shaft 12 with retaining rings 57, the outer rings 13, the middle rings 14 and the one-sided rings 102 can be fastened with threads made on them, in the holes 22 of the housing 7 and / or in sections 48. In the case of using threads on the shaft 12, the partitions 15 are mounted relative to the rings 13, 14, 102 not due to the groove 54, but by pressing them with rings 13, 14, 102 while tightening the thread or other means.

In some cases, the rings 13/14/102 may not be fixed or at least rotatably mounted on the shaft 12 or in the housing 7. This can reduce the relative speed between the interacting parts and reduce their wear. In this case, to reduce the flow between the rings 13/14/102 and the spacer 18, gearing can be performed between them. The teeth can be located at the ends 73 of the separator and on the side walls 36 of the rings 13/14/102.

Depending on the conditions of interaction between the separator and the partition (is the stage tight throughout the cycle), the windows of the entrance 44 and exit 45 can be located either only on spherical part 35, or go to the side walls 36. For example, with a version that does not provide for the tightness of the step throughout the cycle, and if there are walls 36 on the rotor 11, to expand the windows 44, 45, they can be performed on the spherical part 35 and side walls 36.

The machine of FIG. 30 operates as follows. From the open annular cavity 37 by the partition wall 15, in the cavity 23 of the housing 127 around the spherical portion 35 of the rotor I, a working cavity 37 is formed, which is blocked by the separator 18 with its inner part 82 protruding from the groove 24 of the housing 127. Moreover, it blocks it due to the interaction of its opening 75 with a spherical part 35, ends 73 of the separator 18 with the side walls 36 of the rotor 11. Since the separator 18 is mounted in the groove 24 of the housing 127 to rotate in the plane of the groove 24, when the rotor 11 rotates, the plane of the separator 18 does not change its position relative to the housing 127, and its slot 78, due to the interaction of the SSE 20 with the guide groove 130, follows the partition 15 of the rotor 11. The partition 15 moves the boundaries of the working cavity 37 relative to the housing 127, and therefore relative to the separator 18. Thus Thus, a decreasing working chamber 100 is formed in front of the partition 15, and a chamber 101 increasing in size is formed behind the partition 15. The working body enters the chamber 101 from the entrance window 44 located behind the partition 15. To the entrance window 44 it enters from the feed channel 41. From the chamber 100, the working fluid exits through the exit window 45 located in front of the partition 15. From the exit window 45 it enters the discharge channel 41.

In all OPM variants, the separator 18 is a passive element, not loaded with torque from the side of the working fluid (with the exception of a small moment of forces associated with the thickness of the separator 18). Torque from the side of the working fluid is perceived or transmitted by the partitions 15 of the rotor 11, playing the role of pistons.

Claims

Claim

1. Volumetric rotary machine containing

a body with a sphere-shaped cavity and a circular groove around it,

a rotor with at least one spherical part, and at least one partition on it, mounted in the housing for rotation, and the plane of the circular groove extends at an angle with respect to the axis of rotation of the rotor,

a separator with an opening for the spherical part of the rotor and a slot for the partition mounted in a circular groove, with the possibility of rotation relative to the housing in the plane of the circular groove, protruding into a sphere-shaped cavity,

in the body cavity, around the spherical part of the rotor, a working cavity is formed, which the separator divides into parts in which, due to rotation with the rotor, the partition moves,

moreover, on the rotor on one side of the partition is the entrance window, and on the other side of the partition is the exit window of the working fluid.

2. The machine according to claim 1, in which the input and output windows are located on the surface of the spherical part of the rotor.

3. The machine according to claim 1, in which for the supply / removal of the working fluid to the working cavity, channels are made inside the rotor.

4. The machine according to claim 3, in which several steps are made on the common rotor, and the channels pass through all the steps, and one of the channels is blocked off by a plug between adjacent steps.

5. The machine according to claim 4, in which the input of the working fluid is made at one end of the rotor, and the output of the working fluid is made at the other end of the rotor.

6. The machine according to claim 1, in which at least one power synchronizing element is installed in the slot of the separator to improve the synchronization conditions of the separator with the rotor.

7. The machine according to claim 6, in which the power sigofovdziem element, to increase the shoulder holding forces, is attached with the possibility of rotation to the rotor using the axis.

8. The machine according to claim 6, in which the power synchronizing element is made in the form of a cylinder cut from one end with a groove and having a hole for the axis passing through the groove for fastening to the rotor.

9. The machine according to claim 6, in which the power synchronizing element is made in the form of a shaft installed in the rotor and passing to the separator through the input or output window of the working fluid.