WO2011090408A1 - Machine volumique rotative - Google Patents

Machine volumique rotative Download PDF

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Publication number
WO2011090408A1
WO2011090408A1 PCT/RU2011/000031 RU2011000031W WO2011090408A1 WO 2011090408 A1 WO2011090408 A1 WO 2011090408A1 RU 2011000031 W RU2011000031 W RU 2011000031W WO 2011090408 A1 WO2011090408 A1 WO 2011090408A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
separator
axis
piston
rotation
Prior art date
Application number
PCT/RU2011/000031
Other languages
English (en)
Russian (ru)
Inventor
Александр Владимирович ДИДИН
Илья Яковлевич ЯНОВСКИЙ
Original Assignee
Didin Alexandr Vladimirovich
Yanovskij Ilja Yakovlevich
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Didin Alexandr Vladimirovich, Yanovskij Ilja Yakovlevich filed Critical Didin Alexandr Vladimirovich
Priority to UAA201210054A priority Critical patent/UA103721C2/ru
Priority to CA2788321A priority patent/CA2788321A1/fr
Priority to US13/575,188 priority patent/US20130202469A1/en
Priority to CN2011800114613A priority patent/CN102782254A/zh
Priority to EP11734926A priority patent/EP2530241A1/fr
Publication of WO2011090408A1 publication Critical patent/WO2011090408A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C9/00—Oscillating-piston machines or pumps
    • F04C9/005—Oscillating-piston machines or pumps the piston oscillating in the space, e.g. around a fixed point
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/18—Control of, monitoring of, or safety arrangements for, machines or engines characterised by varying the volume of the working chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C9/00—Oscillating-piston machines or engines
    • F01C9/005—Oscillating-piston machines or engines the piston oscillating in the space, e.g. around a fixed point
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/16—Wear

Definitions

  • the invention relates to the field of mechanical engineering, namely to rotary volumetric machines that can be used as pumps,
  • compressors hydraulic drives, including adjustable ones.
  • Known volumetric rotary machine comprising a housing, a rotor and at least one piston, the entrance and exit windows of the working fluid.
  • the rotor has a working surface limited by the surface of rotation, and is mounted in the housing for rotation.
  • At least one partially spherical working cavity is formed, limited by a part of the sphere-shaped surface of the housing, the separator surface and the rotor working surface.
  • the rotor has at least one groove, made mainly along the axis of rotation of the rotor on its working surface.
  • the piston is installed in the said groove of the rotor with the possibility of performing rotational vibrations relative to the rotor.
  • the piston, protruding from the groove of the rotor, has the ability to overlap the working cavity.
  • the separator has the ability to rotate in a sphere-shaped working cavity to change the feed of the machine.
  • the piston has an asymmetric shape, and the resulting irreparable displacement of the center of mass from the axis of the rotational oscillations of the piston, leading to a displacement of the center of mass from the axis of symmetry of the rotor during rotational vibrations of the piston, causing significant centrifugal forces acting on the center of mass of the piston and the resulting moments of forces around the axis of the piston.
  • the latter load the friction pair of the piston - separator or, in the presence of a sealing synchronizing element (SSE), the friction pair of the piston - SSE - separator. It is the wear of the mentioned friction pairs that determines the life of the machine.
  • the disadvantages include the cantilever mounting of the machine shaft in the presence of an uncompensated radial load on the free end of the rotor; the inconstancy of the machine’s feed over one revolution of the shaft and the inability to obtain a uniform feed when several stages are combined in parallel; the impossibility of creating pressure in one step in the variant with one piston; reduction of the maximum pressure developed by the stage when using two pistons due to their weakening, associated with the need for mutual overlap inside the rotor; limited piston travel when using two pistons, reducing maximum feed and control limits.
  • SSE sealing synchronizing element
  • the use of a common sealing synchronizing element (SSE) for two (several) pistons requires the presence of elastic elements through which the piston interacts with the SSE, which limits the scope of the machine.
  • Known ORM (RU 2202695) containing a stator; working chambers; rotor mounted for rotation; the separator mounted for rotation, and the geometric axis of rotation of the rotor and the separator intersect at an acute angle; entry windows and exit windows of the working fluid; moreover, the separator is engaged with the rotor through a sealing synchronizing element (U SE) having a through slot through which the rotor passes.
  • U SE sealing synchronizing element
  • This ORM has a symmetrically loaded SSE, its two stages during parallel operation can provide an almost uniform supply, however, it has increased dimensions (diameter) due to the groove, which makes it possible to rotate the separator. The diameter is further increased due to the need to pass two channels for the working fluid to bypass this groove for communication of the working chambers and steps.
  • the disadvantage is the possibility of concentration of the abrasive by centrifugal forces in the said groove.
  • ORM (RU 2382884), comprising a housing with a sphere-shaped inner working surface, conventionally divided into a bypass and pressure parts, a rotor with a working surface of rotation mounted in the housing with the possibility of rotation, an annular working cavity formed by the working surfaces of the housing and rotor, C-shaped a separator installed in part (along the rotor) of the annular working cavity at an angle to the plane of rotation of the rotor and fixedly attached to the housing, while the working cavity is divided into two parts in the bypass case, and the entrance and exit windows of the working fluid are located on opposite sides of the specified separator, and at least one groove is made on the working surface of the rotor, mainly along the geometric axis of rotation of the rotor, a piston is installed in each groove of the rotor with the possibility of overlapping (sealing) working cavity and performing rotational vibrations in the groove plane, the piston made in the form of at least part of the disk, and each piston has at least one slot for the passage of
  • the working chambers are cut off by a piston and a separator when it interacts with a conical surface on the rotor, because the working cavity is divided by a separator into two parts in the bypass part of the housing.
  • This ORM has reliable synchronization, a symmetrical balanced piston, working bodies with a large margin of safety, almost strictly uniform flow even with one step.
  • the maximum pressure withstand one stage, and the resource is limited by the wear resistance of the friction pair of the SSE - piston due to the load of the SSE differential pressure of the stage. Since the main supporting surfaces of the SSE are located inside the piston part that does not protrude from the rotor, and the pressure drop falls on the parts of the SSE located in the piston slot, the specific pressure on the supporting surface is somewhat greater than the differential pressure of the stage.
  • ORM does not have an adjustable design.
  • Known ORM (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 washer mounted motionless in the housing at an angle to the geometric axis of rotation of the rotor and dividing the working cavity into two parts, and on the working at least one groove is made along the rotor surface along its geometrical 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 geometrical axis intersecting the geometrical axis of the rotor, and the piston is made in the form of at least at least part of the disk, and in each piston there is at least one sealable slot for the passage of the separator.
  • the entrance and exit windows of the working fluid the entrance and exit windows of the working fluid
  • This ORM has reliable synchronization.
  • the ORM has a pulsating feed, which cannot be turned into strictly uniform, by installing several parallel steps.
  • This ORM is the closest analogue.
  • the objective of the invention is to reduce the load on the friction pair to increase the resource and the working pressure drop per stage in the ORM with a sphere-shaped working chamber and a piston performing rotational vibrations relative to the rotor, in their unregulated and adjustable design.
  • the objective of the invention is achieved by the fact that in the annular (circular) sphere-shaped working cavity formed in the housing around the rotor, the working chambers are cut off by a separator and a piston, excluding the participation of the conical surface of the rotor. For this, either a sufficient gap is left for the working fluid to pass between the ends of the separator guide part and the rotor (its conical or its replacing surface), or channels are made on the rotor that allow the working fluid to pass between the parts of the working chamber and / or from the chamber to the entrance and exit windows . Accordingly, the arrangement of the entry windows and exit windows changes.
  • the windows When working with a conditionally incompressible fluid, when executed on the surface of a sphere-shaped cavity of the body, the windows are located in the region of the maximum angle tilt of the separator, in contrast to the location of the windows at the analogue, where they are adjacent to the place of contact of the ends of the separator with the rotor.
  • windows of one of the types are reduced, and the restriction on their position becomes less rigid.
  • the volumetric rotary machine comprises a housing
  • a separator installed in the housing having a guide part with an opening for the rotor
  • a piston mounted in the groove of the rotor with the possibility of performing rotational vibrations relative to the rotor around an axis crossing the axis of rotation of the rotor mainly at a right angle, having at least one slot for the passage of the guide part of the separator,
  • the volumetric rotary machine comprises a housing; rotor mounted in the housing with the possibility of rotation; a separator installed in the housing having a guide part with an opening for the rotor; a piston mounted in the groove of the rotor with the possibility of performing rotational vibrations relative to the rotor around an axis crossing the axis of rotation of the rotor mainly at a right angle, having at least one slot for the passage of the guide part of the separator;
  • the windows of the entrance and exit of the working fluid, and at least one of the windows in the angular position adjoins the place of maximum inclination of the guide part of the separator.
  • the volumetric rotary machine comprises a housing, a rotor mounted in the housing with the possibility of rotation, having a groove mainly along the axis of rotation,
  • a separator having a guide part with an opening for the passage of the rotor mounted in the housing
  • a piston having two slots for the passage of the guide part of the separator, mounted in the groove of the rotor with the possibility of performing rotational vibrations relative to the rotor, when interacting with the guide part of the separator,
  • each chamber exit channels for the passage of the working fluid, made in the rotor with the possibility of its connection with the windows of entry and exit.
  • the objective of the invention is achieved in that the inlet and outlet windows of the working fluid are located in the zone of interaction with the rotor, and on the rotor there are channels configured to connect the working chambers with the inlet and outlet windows, which made it possible to maintain the pressure with one stage when using one piston.
  • the objective of the invention is achieved in that the piston contains at least one sealing synchronizing element installed in the slot through which it interacts with the guide part of the separator.
  • the objective of the invention is achieved in that the sealing synchronizing element is mounted in the piston with the possibility of rotation about an axis perpendicular to the axis of the piston.
  • the objective of the invention is achieved in that the guide part of the separator is installed in the housing at a fixed angle to the axis of rotation of the rotor.
  • the objective of the invention is achieved by the fact that the separator is installed in the housing with the possibility of changing the inclination of the guide part to the axis of rotation of the rotor to control the flow of the machine.
  • the objective of the invention is achieved in that the separator changes the inclination of the guide part to the axis of rotation of the rotor, turning around an axis perpendicular to the axis of rotation of the rotor.
  • the objective of the invention is achieved in that the separator is made with a shell.
  • the objective of the invention is achieved in that the separator of at least one stage is supplemented by a shell with a sphere-shaped cavity.
  • the objective of the invention is achieved in that the guide part is located at an angle with respect to the shell and changes its inclination to the axis of rotation of the rotor, due to rotation of the shell around an axis passing at an angle to the axis of rotation of the rotor.
  • the objective of the invention is achieved by the fact that a sleeve is installed in the housing on which the input and output windows of the working fluid are located, and the machine is equipped with a mechanism for turning the separator and the sleeve.
  • the objective of the invention is achieved in that the separator changes the inclination of the guide part to the axis of rotation of the rotor, turning around a point - the center of a sphere-shaped working cavity.
  • the load of the SSE by the pressure of the working fluid is completely symmetric, which sharply reduces the load on the friction pair of the SSE - piston. Additionally, the working conditions of the piston-rotor friction pair are improved. Due to the changed nature of the load (direction, cyclicity), the possibility of hydrodynamic unloading of the piston (effective if the rotor speed does not decrease below the minimum) and, in another embodiment, full hydrostatic unloading of the piston (effective at any speed). All this allows you to increase the maximum pressure created by the step when working with an abrasive.
  • Figure 1 presents in isometry the stage of a multi-stage volumetric rotary machine (ORM). Removed part of the body.
  • Figure 2 presents in isometric part of the rotor corresponding to one stage
  • FIG 4 presents in isometric sealing power element (U SE).
  • FIG. 5 a separator is shown in isometry.
  • FIG. 6 is an isometric view of a portion of the body visible in FIG. 1.
  • Fig.7 presents in isometric part of the body, missing in Fig.1.
  • FIG. 9 presents in isometry a hydraulically unloaded piston assembly with SSE.
  • Figure 10 presents in isometric part of the housing of the stage, made with the possibility of adjusting the flow.
  • FIG. 11 is a perspective view of a pivot shaft of a spacer.
  • FIG. 12 is a perspective view of a spacer used with the rotary shaft of FIG. 11.
  • Fig presents in isometric two stages of an adjustable ORM with a sphere-shaped shell separator. The near parts of the cases are removed.
  • Fig presents in isometric two stages of an adjustable ORM in Fig.14. All parts are removed except for the far parts of the housings, the halves of the divider with the shell and the rails.
  • Fig presents in isometric diagram of the regulation of the supply of ORM. Shown are two rotor stages with rotary dividers, a hub and a rail.
  • FIG. 30 is an isometric view of the ORM of FIG. 27 from the reverse side.
  • overlap is meant a sliding contact or a small gap.
  • 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.
  • a sphere-shaped cavity is understood to mean a cavity in which at least one of its limiting surfaces is a sphere-shaped surface.
  • the area of interaction of two parts will be called one or more surface sections of one part, with a working gap from which, during operation, the surface of the second part is constantly or periodically able to be.
  • the working gap will be called the gap between the two parts, in which they have the possibility of relative movement, but at the same time there are no leaks of the working fluid through it or are within the limits acceptable for this device due to the smallness of the gap or due to the location of the seal elements in it.
  • the working surface of the part will be called one or more surface sections of one part along which it interacts with other parts to cut off the volume
  • a chamber-forming surface is the surface that limits the working cavity.
  • the working cavity is a limited volume, divided into working chambers by a piston and a separator.
  • a chamber-forming cavity is a limited volume in which the piston moves, dividing it into working chambers. Moreover, for the convenience of description, the passages for the working fluid will be considered separate elements.
  • 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, cavities obtained by casting or in another way.
  • the ORM stage (Fig. 1), which can also be used as a separate pump, contains a housing 1 with a separator 2, a rotor 3 and a piston 4.
  • the piston 4 includes a synchronizing sealing element 5 (U SE).
  • the chamber-forming surface of the rotor 3 (Fig. 2) is made in the form of a surface of revolution and consists of several surfaces concentric with the geometric axis 6 of rotation of the rotor 3: a central sphere-shaped surface 7, two identical truncated conical surfaces 8, resting on opposite sides on a central sphere-shaped surface 7 with lesser grounds.
  • the transition between the cylindrical surfaces 9 and the large bases of the truncated conical surfaces 8 is made along sphere-shaped surfaces 11, the center of which coincides with the center of the central sphere-shaped surface 7.
  • the chamber-forming surface of the rotor 3 forms a circular groove 12 on the rotor 3, the side walls of which are truncated conical surfaces STI 8, and the bottom is the central sphere-like surface 7.
  • a sphere-shaped surface 11 and parts of the cylindrical surfaces 9, a through, almost rectangular (not including rounding at the corners) groove 13 is made.
  • two bypass channels 14 are made in the form of grooves. The angular extent around axis 6 of each of them is% of turnover.
  • the piston 4 (FIG. 3) has the shape of a flat disk with a sphere-shaped side surface 15 and flat ends 16.
  • the diameter of the side surface 15 is approximately (accurate to working clearances and tolerances) equal to the diameter of the sphere-shaped surface 11.
  • the thickness of the disk corresponds to the size of the groove 13.
  • Parallel to the ends 16, a through cylindrical hole 17 is made symmetrically along the diameter in the disk 17.
  • Two cylindrical holes 18 of larger diameter are coaxially aligned with it on two sides. Their diameter is slightly larger than the thickness of the disk.
  • the transition 19 between the different diameters of the holes 17, 18 is made conical.
  • a groove with a sphere-shaped bottom 21 is made, cutting the lateral surface of the disk and forming a through slot 22.
  • the diameter of the bottom 21 corresponds to the diameter of the central sphere-shaped surface 7.
  • Chamfers 23 are formed between the ends 16 and the surface of the holes 18.
  • the geometric axis of symmetry of the disk, perpendicular to the ends 16, is the axis 161 of its rotational vibrations relative to the rotor 3.
  • SSE 5 (Fig. 4) is made in the form of a symmetrical dumbbell, consisting of two coaxial cylinders 24 connected by an axis 25 of a smaller diameter. The transition between the cylinders 24 and the axis 25 is executed along the cone 26.
  • the cylinders 24 are symmetrically dissected by a circular flat groove 27 extending to their outer ends 28.
  • the bottom 29 of the groove 27 is spherical.
  • the external ends 28 of the cylinders 24 dissected by the groove 27 are bounded by a sphere-shaped surface, which has a diameter close to the diameter of the side 15 of the piston 4.
  • the sides 30 of the groove 27 are flat.
  • the SSE 5 in the region of the middle of the axis 25 is divided into two parts (not shown) that are connected during assembly by any known method (resistance welding, welding through a process hole, threaded or pin connection).
  • the separator 2 (figure 5) is made in the form of a flat rectangle with rounded corners with an opening 31 in the center.
  • the surface of the hole 31 is spherical.
  • the ends 32 are flat.
  • the central part of the separator 2 in the form of a flat ring (in Fig. 5 is limited by a dash-dotted circle) interacts with the piston 4 through the SSE 5, to cut off the volume.
  • the guide part 140 if necessary, distinguish it from the rest of the separator 2, which serves for its mounting in case 1.
  • Axis 144 is the axis of rotation of the generatrix of the guide part 140.
  • the separator 2 can consist only of the guide part 140.
  • the separator 2 is made of two identical parts (parts) .
  • the connector 33 between them passes through approximately diametrically opposite points of the central hole 31. From them, it goes at an angle to the radius of the hole 31 (in the above example, the angle is 30 degrees).
  • the surface of the connector 33 is made in the form of a symmetric dihedral angle (in the above example, the angle is 90 degrees), the peak 34 of which is oriented against the direction of motion of the SSE 5 during the operation of the ORM.
  • a sphere-shaped cavity 35 with a center on the axis 6, from which two coaxial axes 6 of the cylindrical bore 36 extend for the output of the shaft 10 of the rotor 3 on opposite sides.
  • three annular sections can be embedded on the surface of the cavity 35 : symmetric, coaxial to axis 6 middle section
  • the housing 1 is made of two parts 40 and 41 (Fig. 8), the separation plane 42 between which passes through the axis 6 perpendicular to the groove 39 (Fig. 6, 7).
  • an entry window 43 and a working fluid exit window 44 are located. Each of them has a length of 1 A revolution around axis 6. In the direction along axis 6, the windows 43 and 44 are spaced from the center of surface 35 and are located at extreme portions 38 of surface 35, i.e. outside the zone of the circular groove 12.
  • the entrance window 43 and the working fluid exit window 44 can communicate with the working chambers only by the bypass channels 14. It can be said about the entrance window 43 / exit 44 that it adjoins from two sides a plane passing through the axis 6 rotor rotations 3 perpendicular to the plane passing through the axis 6 and the axis of rotation 144, forming the guide part 140 of the separator 2.
  • the central sphere-shaped surface 7 (Fig. 1), two truncated conical surfaces 8 and the middle portion 37 of the surface of the sphere-shaped cavity 35 form an annular working cavity 45, which the separator 2 divides the guide part 140 into two identical chamber-forming cavities 46 of variable cross section.
  • the piston 4 divides each of the chamber-forming cavities 46 into two working chambers 47 of variable volume.
  • the entrance window 43 and the exit window 44 are approximately in the middle between the maximum and minimum sections of the chamber-forming cavity 46 (we mean sections by planes containing axis 6). Those. in the region of the minimum cross section and in the region of the maximum cross section of the chamber-forming cavity 46 and the regions adjacent to them, there are no entry windows 43 and exit windows 44.
  • the piston 4 with its parts protruding from the rotor 3 creates a pressure drop of the stage.
  • the windows of the inlet 43 and the outlet 44 of the working fluid are located, and these places are not used to create a pressure drop.
  • the truncated conical surface 8 of the rotor 3 does not interact with other surfaces to cut off the working chambers 47, so there are no strict requirements for quality and shape (unlike analogues). On the contrary, between it and the end face 32 of the guide part 140 of the separator 2 there is a large gap - the passage 143 for the working fluid. More general requirements for entry windows 43 and exit windows 44 are that they are located in the area of interaction of the housing 1 with the rotor 3, communicating with the cameras 47 through the bypass channels 14, and individually the angular length of the window
  • each chamber-forming cavity 46 for an incompressible working fluid should be approximately one revolution, and may be less than a revolution for a compressible working fluid.
  • the rotor 3 Since the sum of the angular lengths of the entry window 43, exit window 44 and two bypass channels 14, related to each chamber-forming cavity 46, is approximately equal to one revolution, the rotor 3 has the possibility of almost completely overlapping each of the windows 43, 44. An exception is the case of a high-speed ORM, which there is enough incomplete (for example, 95 percent) overlap of windows 43,
  • the entry windows 43 of the different chamber-forming cavities 46 are symmetrical about the center of the cavity 35.
  • the exit windows 44 of the different chamber-forming cavities 46 are also symmetrical about the center of the cavity 35.
  • the housing 1 is made in the form of a cylinder.
  • a channel 48 is connected that bypasses the cavity 35.
  • a similar channel 49 (Fig. 8) is connected by their exit window 44 on the outer side surface of the housing 1.
  • Both channels 48, 49 are the same and the axis are symmetrical between by myself.
  • Channel 48/49 begins and ends with blind holes 50/51 (FIG. 1, FIG. 8), passing past the cavity 35 parallel to the plane of the connector 42 perpendicular to axis 6. Entrance windows 43 / exit windows 44 are led from the cavity 35, respectively.
  • the channels 48 and 49 have a mainly diagonal (screw) direction.
  • the middle of the 48/49 channel is at connector 42.
  • holes 55 and 56 are made in not extreme steps at each end 52 and 57, and only holes 55 or 56 are filled at the extreme ends of the extreme steps.
  • only holes 55 or 56 are made at each end 52 and 57 of the step.
  • blind shallow holes 60 (Fig. 8) for pins are made instead.
  • the arrangement of channels 48/49 and dividers 2 is mirror-like relative to the plane passing between the steps in the thread region 54 perpendicular to axis 6, and the location of the holes 55 at the extreme end 52 of the first stage 61 is centrally symmetrical to the holes 56 at the extreme end 57 of the second stage 62.
  • the rotor 3 of a multi-stage ORM is performed by a common (integral) for several stages.
  • the rotor stages 3 of two adjacent ORM stages are deployed around axis 6 in the UA revolution.
  • Separators of 2 different steps are parallel. Couples of steps connected in parallel are hydraulically connected in series.
  • the sphere-shaped surface 11 of the rotor 3 may be absent, and the truncated conical surface 8 may pass into the cylindrical surface 9. Moreover, its diameter (diameter of the shaft 10) may be increased.
  • the bypass channels 14 are performed on the surface 9 or inside the shaft 10 with access to the cylindrical surface 9. Then the entrance windows 43 and the exit windows 44 performed on the surface of the holes 36 under the output of the shaft 10. The surface of the hole 36 should interact with the surface 9 of the rotor 3.
  • the working part of the ends 32 (Fig. 5) of the separator 2 can have a conical surface shape, tapering to the central hole 31. Then the groove 26 (Fig. 4) on the SSE 5 also has mating conical lateral surfaces 30.
  • the separator 2 can and to have small deviations from the plane or from the rotation figure (applications for improving the performance of ORM due to the curvature of the separator are known).
  • piston 4 and SSE 5 the piston 4 may not be flat, but have a thickening in the center.
  • the piston 4 may be provided with an axis coaxial with the geometric axis 161. It may consist of two half shafts. For its fastening, it is easier to use the one-piece connection performed during assembly, for example, welding.
  • the piston 4 may consist of two (several) parts.
  • the connector can extend in the middle of the piston 4 perpendicular to the axis 20 or have a more complex shape.
  • the SSE 5 can consist of two separate halves (then we can talk about two SSE 5), but their mutual fastening reduces the load on the friction pairs, improving the performance of the machine.
  • spacer sleeve 58 instead of using spacer sleeve 58, shims can be used or just fine-tune / run the step length. Reducing sleeves 59 in these cases are also not needed.
  • protrusions 64 (Fig. 9) adjacent to the groove 27 and expanding its side surfaces 30 can be made on the lateral side of one or two SCH 5 cores 24.
  • Chamfers 23 on the piston 4 must be increased.
  • a symmetrical groove 65 is made on one side of the axis 20 along the perimeter of the surface portion, which does not come out of the groove 13 when the piston 4 rotates, if the end face 16 of the piston 4 is conditionally divided into a central circle of maximum diameter that does not cut through the slot 22 and two half rings adjacent to it, then this circle and the middle (along the corner) of the half rings remote from the slots 22 of the piston 4 do not leave the groove 13.
  • the groove 65 consists of an arc along the lateral side 15, symmetrical relative to its two almost radial sections, two symmetric arcs along the perimeter of the circle (bottom 21), and a straight section along the axis 20.
  • a groove 65 symmetrical to it is filled.
  • grooves 66 open to the slots 22 are made.
  • the same system of grooves 65 and 66 is carried out at the other end 16.
  • the grooves 65 are connected with holes 67 to the grooves 66 on the other side of the piston 4.
  • the piston 4 can be made of two parts 68, the connector between which is made on the plane of symmetry of the piston 4 parallel to its ends 16. The parts are fixed relative to each other by pin screws 69 located around the perimeter of the piston 4, or by welding.
  • the groove 39 is not performed.
  • the transition 73 between the holes 70 and 71, as well as the transition between the holes 70 and 72 are spherical.
  • a part is placed - a rotary half shaft 75 (Fig. 13) in the form of a cylinder 76 (Fig. 11), ending with a larger diameter concave hat 77.
  • the concave surface 78 of the cap 77 is a continuation of the surface of the cavity 35.
  • a convex cap 79 is pressed onto the cylinder 76 during assembly, having a central hole for the cylinder 76.
  • the hole on the cap 79 is elongated by a cylindrical protrusion that extends into the hole 70.
  • the groove 80 in the center has a recess going into the cylinder 76.
  • the surface 81 of the cap 79 has teeth 82.
  • the separator 2 (Fig. 12) is made in the form of a central guide portion 140 in the form of a flat ring with a sphere-shaped outer lateral surface 83, ends 32 and a central hole 31.
  • the separator 2 consists of two identical parts 85, the connector between which goes to the middle the protrusions 84. When pressing into the groove 80, the protrusions hold the parts 85 together.
  • the separator together with the two rotary shafts 75 is able to rotate relative to the housing 1 around the axis 97 (Fig.13), perpendicular to the axis 6.
  • the angle of its possible deviations from the plane of rotation of the rotor from -25 to +25 degrees. The angle is limited only by the shape of the rotor 3.
  • the housing 1 (FIG. 10) of the steps of such an adjustable ORM is performed with a cavity 35 without lowering 53 and the spacer sleeve 58.
  • the length of the housings 1 of the steps 61 and 62 (FIG. 13) is adjusted by the distance between the steps 61 and 62 on the common rotor 3 or is adjusted by adjusting gaskets (not shown).
  • Channels 48 and 49 of steps 61 and 62 are performed in the same way (and not mirror-like, as in the previous example), dividers 2 are set in parallel.
  • the rotors 3 of the hydraulically parallel steps 61, 62 are deployed 1 L revolution. Holes 55/56 (FIGS.
  • two grooves 86 are made parallel to the axis 6.
  • the grooves 86 on the size of the teeth touch the side of the holes 72.
  • the rails 87 with teeth 88 are tightly placed in separate sections.
  • the rails 87 are in gearing with the convex hat 79 of the rotary half shaft 75.
  • two rails 87 are synchronously moved, all the rotary half shafts 75 and the dividers 2 of all ORM stages are synchronously rotated in one direction.
  • Two (and not one) rails 87 are used to relieve part of the load from the separator 2.
  • the rails 87 are connected to a piston pressure regulator or to another control drive.
  • the piston 4, SSE 5 and the rotor 3 do not fundamentally differ from the ORM in figure 1. Small differences can be in the length of the step (without the sleeve 58 it is shorter), the thickness of the piston 4 (the piston 4 may be slightly thinner, since the separator 2 in this embodiment is less durable), etc.
  • a large adjustment angle makes the machine reversible, i.e. the direction of movement of the working fluid by changing the angle of the separator can be reversed.
  • the maximum pressure drop per stage in this design is limited by the strength of the splitter 2.
  • FIG. 14 Another embodiment of the separator 2 (Fig. 14) makes it possible to increase the maximum pressure of the ORM stage.
  • the central guide portion 140 (Fig. 15) of the spacer 2 in the form of a flat ring, with a central hole 31 and ends 32 is enclosed in a sheath 89 with a sphere-like inner surface 90, i.e. the angle of inclination of the guide portion 140 is fixed relative to the shell 89, or the separator 2 is made integrally with it.
  • This design increases the rigidity of the separator 2.
  • the outer surface 91 (Fig.14) of the shell 89 is concentric with the inner surface 90 (Fig.15) and, for convenience, is sphere-shaped.
  • the casing 89 has a central through elongated hole 92 that allows the shaft 10 (Fig. 14) of the rotor 3 to be passed at different permissible angles of inclination of the separator 2 to the plane of rotation of the rotor 3.
  • the hole 92 passes the shaft 10 at angles of inclination of the guide portion 140 of the separator 2 from 0 to 25 degrees.
  • the role of the sphere-shaped cavity 35 in the formation of chamber-forming cavities 46, in this embodiment, is played by the sphere-shaped cavity 93 formed inside the shell 89.
  • the separator 2 supplemented by the shell 89, is made of two parts, a connector 94 (Fig. 15) between which passes approximately through the center of the separator 2 along its rotation plane.
  • the entrance windows 43 and the exit windows 44 remain on the surface of the cavity 35 of the housing 1, which is already may have a different shape, for example, the shape of the surface of rotation relative to the axis 97 of rotation of the separator 2. But it is more convenient to make it * sphere-like.
  • passages 98 symmetrically with respect to the turning plane. They are made in the form of one rhomboid-shaped large opening 99 and several small holes 100.
  • a large hole 99 is made in the area of the shell 89, which for any acceptable angular position of the separator 2 is opposite the input window 43 / output window 44.
  • Small holes 100 are made in sections of the shell 89, which are not at any acceptable angular position of the separator 2 opposite the entry window 43 / exit window 44, i.e. there are provisions of the separator 2, in which small openings 100 may not communicate with the input windows 43 or output windows 44.
  • Such a design of the input / output passages 98 can remove the influence of the angular position of the separator 2 on the bypass phases cars.
  • the overall shape of the passage 98 (with all its openings 99, 100) is similar to a trapezoid.
  • the passages 98 are located symmetrically with respect to the shell 89, but not symmetrically with respect to the guide portion 140 of the separator 2, because it is located at an angle to the plane of symmetry of the shell 89.
  • the concept of a small hole 100 is qualitative, because the optimal size depends on the viscosity of the working fluid, the proportion of leaks in the machine feed and is determined for each specific application. What is important is the fact that such holes 100 are separate, i.e. that they do not merge with other openings 100.
  • the smaller the size of the openings 100 the greater the accuracy of observing the optimal phases of the bypass of the working fluid, but the greater the percentage of hydraulic losses.
  • the larger the size of the holes 100 the less accurate the observance of the optimal phases of the bypass of the working fluid, but the smaller the percentage of hydraulic losses on them.
  • the large hole 99 can also be replaced with a set of small holes, although this slightly increases the hydraulic resistance.
  • Small holes can be located on other parts of the shell 89 to equalize the pressure inside and outside the shell 89. This allows you to reduce the load on the shell 89 from the pressure drop of the working fluid and, thereby, reduce its required thickness and, accordingly, the weight and dimensions of the machine. In this case, the pressure difference is perceived by the housing 1, which in any case is designed for this.
  • the input windows 43 and the output windows 44 are located in the interaction region 38 of the housing 1 with the rotor 3. But the housing 1 interacts with the rotor 3, in this embodiment, through the intermediate part - the shell 89 of the separator 2, which seals the contact of the housing 1 with the rotor 3, but thanks to the passages 98, it passes the working fluid in the direction between the channels 14 (figure 2, 14) of the rotor and the input windows 43 / output windows 44 located on the housing 1. That is, hole-shaped shell 89 prevents the passage of the working fluid along the gap between the housing 1 and the rotor 3 and passes it in the transverse direction. To limit the degrees of freedom of the separator 2 in the cavity 35, there are two half shafts 101 (FIG.
  • teeth 82 are made on the cylindrical surface of the flanges 95.
  • the inclination of the separator 2 is controlled by the rail 87, placed in the groove 86 of the housing 1, located at the junction of parts 40 and 41, and touching the size of the teeth 82 grooves 96 steps 61, 62.
  • the supply of the working fluid is made by means of the supply channels 103 (Fig. 16) and the discharge channels 104, extending along the surface of the housing 1 along the axis 6 along the steps 61, 62.
  • Two discharge channels 104 pass symmetrically on both sides of the groove 86, and diametrically from the the opposite line of the connector 42, there are two supply channels 103. In fact, this is one channel 103, but for the symmetry of the insertion into the pipe 63 (shown earlier in Fig. 8), it has a stiffener 105 in the middle.
  • Connector 42 from the diametrically opposite side of groove 86, has a cylindrical hole 107 for a tube gasket that hydraulically connects the ORM to the outlet for low / high pressure supply for axial unloading of the rotor 3.
  • the shape of the outer surface 91 and the surface of the cavity 35 in this embodiment need not be sphere-shaped. These surfaces can be any surfaces of revolution relative to axis 97, for example, cylinders. But the sphere-like design allows to reduce the size and weight.
  • the shell 89 of the separator 2 is made in the form of a software ring.
  • the inner surface 90 of the PO ring is bounded by a sphere-shaped surface that is close (up to tolerances) in diameter to the diameter of the cavity 35.
  • the outer surface 91 is also spherical and concentric with the inner surface 90, the ends 136 flat.
  • the guide portion 140 of the spacer 2 is in the ring 110 at an angle to it, i.e. installed at a fixed angle, for example, using a groove, or made integrally. Those.
  • the central hole 31 is concentric with the inner surface 90, and the ends 32 (or the plane) of the guide part 140 of the separator 2 are located at an angle (in this example, 21 degrees) to the ends 136 of the ring 110.
  • the body portion 1 is an inclined ring 110 together with the guide part 140 of the separator 2 installed therein, is allocated in a separate part - the rotary separator 111 (used further in Fig.21, 26). In this case, on the housing 1 (Fig.
  • a groove 112 is performed, which passes symmetrically through the center of the cavity 35, at an angle (in this example, 21 degrees) to the plane of rotation of the rotor 3 (in other words, the axis of rotation of its generatrix passes at an angle to axis 6) . It is bounded by a sphere-shaped lateral surface 113, concentric cavity 35, and two ends 114 in the form of flat rings.
  • the groove 112 is made symmetrically relative to the plane of the connector 42.
  • the rotary separator 111 (Fig. 17) is made of two parts 115 and 116.
  • the connector 117 between them passes through the entire part through and through approximately the center of the guide part 140 of the separator 2, parallel to the plane of symmetry rotary separator 111, in the form of a dihedral angle 118, and then, on one side of the plane of symmetry symmetrically to the plane of the guide part 140 of the separator 2, on both sides of the body of the guide part 140 along the ring PO, forming rectangular protrusions 119 in it, about itelno diametrically opposite positions part 115 and response slots for his part 116.
  • teeth 122 are made in a portion adjacent to the connector 117 with an angular extent of approximately 100 degrees about the axis of symmetry of the ring 110.
  • a groove 86 is made along axis 6 with a section in the form of a ring sector.
  • the groove 86 touches the size of the tooth 122 groove 112 in the place of its maximum inclination.
  • the rail 87 (Fig.19), having a cross section corresponding to the cross section of the groove 86, in the form of a sector of the ring.
  • teeth 123 are made for interacting with teeth 122. In this example, teeth 123 are made at an angle of about 45 degrees to axis 6.
  • the direction of movement of the rail 87 in the groove 86 partially coincides with the direction of rotation of the ring PO, which improves conditions their gearing.
  • the guide part 140 of the separator 2 changes the angle of inclination to the plane of rotation of the rotor 3, changing the feed of the OPM, but there is also a negative effect - the maximum inclination of the guide part 140 of the separator 2, with the angular position of which the position of the entry windows 43 and the exit windows 44 of the working fluid.
  • the input window 43 and the output window 44 are performed on the rotary sleeve 124 (Fig.20).
  • the rotary sleeve 124 is in the form of a pipe segment with concentric cylindrical inner and outer surfaces.
  • the diameter of the inner surface is close to the diameter of surface 9. They interact with each other. It symmetrically executed two input windows 43 and two output windows 44.
  • the entry windows 43 are symmetrical to the exit windows 44 and the pair of windows 43, 44 is centrally symmetrical with respect to the center of the sleeve 124 to the other pair of windows 43, 44.
  • the angular length of each window 43, 44 is a revolution around the axis of the sleeve 124.
  • the sleeve 124 perpendicular to its axis, concentric with the sleeve 124, is a protrusion 125 in the form of a sector of a flat ring with teeth 126 on the outer cylindrical surface (in other words, the gear sector).
  • the teeth 127 are machined corresponding to the teeth 126. They are made at a smaller angle to the rail 87 than the teeth 123.
  • the ratio between the angles of the teeth 123 and teeth 126 is calculated from the condition that the rotary sleeve 124 should be rotated by the rail 87 relative to the axis 6 twice as slow as the rotary divider 111 is rotated by the rail 87 in the groove 112.
  • the sleeve 124 (Fig. 20) is made of two parts.
  • the connector 120 between them is symmetrical about the plane of symmetry of the sleeve and passes through the inner surface of the sleeve 124 in its diametrically opposite places away from the windows 43, 44, along the radius, then at right angles to it and then again at right angles in the same direction, forming steps.
  • the parts of the sleeve 124 are connected using pins for which radial holes are made in the step of the connector 120.
  • the stiffness of the sleeve 124 is provided due to the thickness of its walls.
  • the half-shafts 10 (Fig. 21) of the rotor 3 are larger in diameter than in the ORM of Fig. 1, because channels 14 for the passage of the working fluid, starting on truncated conical surfaces 8, are filled inside the rotor 3 and go out in the form of windows 128 already on the cylindrical surface 9.
  • the angular length of the windows in this example is V * rotation around axis 6.
  • In the middle of the window 128 is left stiffener 129.
  • Channels 103 the supply and channels 104 (Fig.19) of the removal of the working fluid is made on the outer surface of the housing 1 in the axial direction.
  • the two channels 103 are adjacent to the groove 86, and the two channels 104 are on the opposite side of the housing 1 and are separated by a stiffener 105.
  • the channels 103 and 104 are interchanged.
  • an opening 107 passes through all the stages of the ORM to communicate the ORM entry region with the ORM exit region. Through it, from one region to another, the pressure necessary for the hydraulic axial unloading of the common rotor 3 and for the drive of the rail control system 87 (feed ORM) is applied.
  • a cylindrical cavity 130 under the sleeve 124 having a diameter close to the diameter of the outer surface of the sleeve 124.
  • Passages 131 for the working fluid from the channels 103 and 104 go to its surface (Fig. 19 ) to the area of the windows 43 and 44, respectively.
  • the passages 131 go to the outer surface of the housing 1 between channels 103 and 104 and have an exit either to channel 103 or to channel 104, depending on the position of the stage in the ORM and the position of the passage 131 on it.
  • the outer surface of the sleeve 124 interacts with the surface of the cavity 130.
  • In the center of the cavity 130 there is a flat groove 132 for the protrusion 125.
  • the angular length of the groove 132 is greater than the angular length of the protrusion 125 by the angle of regulation (in this example, 34 degrees).
  • the corresponding channels of different stages communicate with each other, and at the junctions of the hydraulically sequential stages, only the channel 104 for the outlet pressure of one stage is communicated with the channel 103 for the inlet pressure of the next stage.
  • the channels 103 and 104 of the hydraulically sequential steps necessary for joining are opposite each other.
  • the input windows 43 and the output windows 44 are located on the housing 1 in the region of its interaction with the rotor 3, but they interact through an intermediate part - a sleeve 124, which seals their contact. But in addition to the previous embodiment, the sleeve 124 actively shifts the boundaries of the entry windows 43 and exit windows 44.
  • FIG.22 Another way to control the sleeve 124 (Fig.22) is the implementation of a screw groove 133 on the sleeve 124 in the interval between the windows 43, 44 instead of the protrusion 125. Then, on the rail 87 instead of the teeth 127, a high tooth 134 is made to interact with the screw groove 133. On the housing 1 instead of groove 132, a through groove running along axis 6 inside the groove 86 along the length of the cavity 130. Tooth 134 has two lateral surfaces corresponding to the helical groove 133 and two lateral surfaces corresponding to the groove in the housing 1.
  • the pressure difference is limited by the strength of the separator 2, the angle of the machine of FIG. 14 is limited, and the machine of FIG. 19 has an extra detail - the bypass sleeve 124.
  • the next version of the machine (FIG. 26) is devoid of these disadvantages.
  • the central guide portion 140 of the separator 2 (Fig. 23) in the form of a flat ring, with a central hole 31 and ends 32, is enclosed in a shell 89 with a sphere-shaped inner surface 90 and a concentric sphere-shaped outer surface 91.
  • the shell 89 there is a round central through hole 92, allowing the shaft 10 of the rotor 3 to be passed at zero and at the maximum allowable angle of inclination of the guide part 140 of the separator 2 to the plane of rotation of the rotor 3.
  • the hole 92 passes the shaft 10 at angles of inclination of the direction
  • the part of 140 is from 0 to 25 degrees.
  • the role of the sphere-shaped working cavity 35 in the formation of chamber-forming cavities 46, in this embodiment, is played by the sphere-shaped cavity 93 formed inside the shell 89.
  • protrusions 135 On the surface of the sheath 89 teeth 138 (grooves) are made, the inclination of which to the axis 137 changes (as with a helical gear, only the inclination of teeth 138 smoothly changes from tooth to tooth).
  • the separator 2 In order to be able to assemble the machine, the separator 2, supplemented by the sheath 89, is made of two parts, the connector 117 between which extends approximately through the center of the guide part 140 of the separator 2 and consists of rectangular protrusions 119 along the plane of the separator 2 and its corresponding grooves. On one of the protrusions 119 in the center of the separator 2, two dihedral angles 118 are made with vertices directed in opposite directions in the direction along the plane of the separator 2.
  • the housing 1 (Fig.24, 25) there is a sphere-shaped cavity 35 for accommodating the shell 89. On the surface of the cavity 35 there are three (by the number of protrusions 135) curved guide grooves 139. On the surface of the openings 36 of the housing 1 there are entrance windows 43 and exit windows 44 working fluid. Their angular extent is approximately a revolution. On the outer surface of the housing 1 there is a groove 86 under the rail 87, running along the axis 6. On two sides relative to the groove 86, the channels 103 and 104 are symmetrically located. Each of them has a stiffener 105 in the middle. For assembly, the housing 1 consists of two parts 40 and 41. The connector plane 42 between them passes through stiffeners 105. The groove 86 is in the center of part 40. The input windows 43 and output windows 44 are symmetrically located on parts 40, 41 and are connected by passages 96 with channels 103 and 104, respectively.
  • the guide portion 140 of the separator 2 (FIGS. 23 - 26) changes its inclination to the plane of rotation of the rotor 3 when the separator 2 is rotated around a point — the center of the cavity 35. It does not have a fixed rotation axis. Having an additional degree of freedom, he performs two movements simultaneously - a tilt (as with the machines in Figs. 10-13 and 14) and a rotation about the axis of symmetry of the shell 89 (like with the machines of Figs. 17-22). He leans from -25 degrees through zero again to -25 degrees, as the hole 92 allows him, but he manages to turn around axis 6, as a result of which a negative slope of -25 degrees becomes positive at +25 degrees.
  • Guide grooves 139 can be constructed by following the path of the protrusions 135 while tilting and rotating the spacer 2. Their shape depends on the position of the protrusions 135.
  • the protrusions 135 may be in the shape corresponding to the grooves 139 (it is easy to obtain by running the protrusion 135 with the groove 139), or they can be mounted rotatably, or an intermediate element, for example, a sleeve, can be worn to transmit forces on a cylindrical protrusion 135.
  • the protrusions 135 can be performed on the surface of the cavity 35, and the guide grooves 139 on the shell 89. There can be many protrusions and grooves.
  • the space in the hole 92, free from the shaft 10 of the rotor 3, can be filled with a separate part, having the shape of a spherical circle with a radial hole for the shaft, offset from the center.
  • each stage 61, 62 it is possible in each stage 61, 62 to use to create a pressure drop only part of the duty cycle having a maximum feed (Fig. 27).
  • the windows of the entrance 43 and exit 44 can reach the groove 39 under the separator 2. Since the windows 43, 44 are large, a stiffener is left in the middle of the windows 43, 44 for the stiffness of the housing 1.
  • the load of the piston 4 and SSE 5 is similar to the load in the previous versions, except that on the part of the cycle, due to the extension of the connection of the working chambers 47 with the inlet and outlet windows 44, the pressure drop of stage 61, 62 almost completely disappears.
  • two or more successive stages 61, 62 are installed, supporting pressure - each in its own part of the cycle, possibly with a slight overlap. So, for example, if the pressure drop over the entire cycle is provided by two successive stages 61, 62, then for approximately 1/2 cycle the working chamber 47 of the stage is connected simultaneously with the inlet window 43 and the outlet window 44, and if it is three, then approximately 1 / 3 cycles, etc.
  • Stage 62 creating differential pressure, pumps the working fluid through the working cavities 46 which do not create, at this moment, the pressure of the successive stages 61.
  • the channels 14 on the rotor 2, in this embodiment, are used to a greater extent for passage 143 than as a means for connecting the input windows 43 and the output windows 44 with the working chambers 47.
  • the passage 143 is provided with channels 14 rather than a general shift of the truncated conical surfaces 8 into the body of the rotor 3, because Thus, it is possible to maintain a large area of the supporting surface for the piston 4 in the groove 13, because channels 14 do not reach the groove 13.
  • a surface is formed that is not a surface of revolution about axis 6.
  • the machine of FIG. 27 is similar to the machine of FIG. 1.
  • the differences are in the channels 14, expanded in angular size, and the windows of entrance 43 and exit 44, expanded in size (mainly along the axis 6), and a change in the system of channels 48, 49, connecting stages 61, 62 (due to the transition from parallel to serial connection ) Also, to simplify the description, a system for adjusting the distance between steps 61, 62 was not performed.
  • the machine of FIG. 27 can be used in all the adjustable versions described previously for the machine of FIG. the transition from the machine of FIG. 1 to the machine of FIG. 27 consists in increasing the windows of the inlet 43, the outlet 44 and the channels 14 (instead of the channels 14, a large gap between the parts can be used - passage 143).
  • the housing 1 (Fig.29, 30) is made of two parts 40 and 41, the separation plane 42 between which passes through the axis 6 perpendicular to the groove 39.
  • the housing 1 of the machine of Fig.27 is made in the form of a cylinder.
  • channels: 147 - 154 On the outer surface of the housing of the 1st group of two stages 61, 62 pass channels: 147 - 154. Their location is asymmetric.
  • channels 147 - 149 and straight channels 150, 151 pass, on the other side of the casing 1 in parts 41 pass around spherical cavities 35 "c" - shaped channels 152 - 154.
  • Channel 147 (Fig.29, 30) is made of two parts 40 and 41, the separation plane 42 between which passes through the axis 6 perpendicular to the groove 39.
  • the housing 1 of the machine of Fig.27 is made in the form of a cylinder.
  • channels: 147 - 154 On the outer surface of the housing of the 1
  • Channel 29 connects the input window 43 on part 40 of the stage 61 with the input of the machine or with the previous steps.
  • Channel 148 connects the exit window 44 on part 40 of the stage 61 to the nearest entrance window 43 on part 40 of the stage 62.
  • Channel 149 connects the exit window 44 on part 40 of the stage 62 to the exit of the machine or to subsequent stages.
  • Channel 152 (Fig. 30) connects the inlet window 43 on part 41 of stage 61 to the inlet of the machine or to the previous stages.
  • Channel 153 connects the exit window 44 on part 41 of the stage 61 to the entrance window 43 farthest from it on part 41 of the stage 62.
  • Channel 154 connects the exit window 44 on part 41 of the stage 62 to the exit of the machine or to subsequent stages.
  • Fig.27 shows an example of the execution of the machine of Fig.27 in the ground controlled execution. It usually requires fewer steps, as well as machine inlet and outlet nozzles. Therefore, the use of an external pipe as a common machine body is less practical, and transverse separation of the body into parts is preferable.
  • the housing 1 consists of three parts, similar in shape to the cylinders: the middle part 155 and two symmetrical extreme parts 156.
  • the connectors between them pass through the centers of steps 61 and 62 (through the centers of the cavities 35).
  • fasteners holes, bolts
  • the separator 2 is made similar to the separator of the machine of Fig. 14 with a sphere-shaped shell 89. It has a sphere-shaped inner surface 90 and, for ease of execution, a sphere-shaped outer surface 91. There are slight differences in the fastening of the two parts of the separator 2 to each other. The section between them passes symmetrically through the center of the sheath 89, but on one part there is a cylindrical abatement, and on the other a cylindrical protrusion covering it. When assembling, the depreciation enters the protrusion and the parts are fixed to each other by pins (not shown). The inlet windows 43 and the outlet windows 44, to reduce hydraulic resistance, are made on the shell 89.
  • the rotors 3 of the individual steps 61, 62 are made separately. Between them there is a connection of the "shaft - sleeve" type.
  • half-shafts 101 of the separator 2 exit the housing 1 through sealed holes 158 and have flats (splines) 159 at the ends for docking with an external device that controls the flow of the machine.
  • the piston 4 is the groove 13 of the rotor 3 (Fig. 32), flat grooves 141 are made on the piston 4 parallel to its ends 161. Each groove 141 passes through the side surface 15 of the piston 4 without touching the slots 22. When using SSE 5, the grooves 141 do not touch the holes 17, 18 under the SSE 5.
  • the piston is composed of several disks connected in the region of the axis 20 of the SSE 5.
  • the groove 13 for the piston 4 is made in the form of several parallel grooves 145 connected in the middle of the groove 13. Between the adjacent grooves 145 protrusions 142. The thickness of the protrusion 142 corresponds to the size of the groove 141.
  • the protrusions 142 do not completely overlap the grooves 141, leaving a place near the axis 20 for the passage of the working fluid cut off into the groove 141.
  • each groove 141 is made on each side of the SSE axis 5. But you can perform a larger number of grooves 141. In this case, each groove 141 corresponds to the protrusion 142 in the groove 13 of the rotor 3.
  • the grooves 145 may not be flat, for example, conical with the axis of the cone along the geometric axis 161 of the rotational vibrations of the piston 4. That is, the surfaces of the grooves 145 may be surfaces of rotation about the geometric axis 161 of the piston 4. Then, a mating surface is formed on the protrusions 142.
  • Such a piston 4 can also be used in other ORMs from the above analogues, since the addition of grooves 141 does not affect the way or features of the ORM, but only enhances the support of the piston 4.
  • the machine of figure 1 works as follows.
  • a circular working cavity 45 is formed around the rotor 3, which the guide part 140 of the separator 2 is divided into two parts 46 of variable cross section, each of which the piston 4 divides into two working chambers 47.
  • the angle between the piston 4 and the guide part 140 of the separator 2 periodically changes. Therefore, the volume of the working chambers 47 periodically changes.
  • two chambers 47 located centrally symmetrically with respect to the center of the cavity 35 increase their volume, two other working chamber 47 reduces its volume.
  • the channels 14 coming from them are in overlap with the entrance windows 43 (Fig.
  • the machine of FIGS. 10-13 operates in a similar manner.
  • the difference is that using the mechanism for changing the angle of inclination of the separator 2 (more precisely, its guide part 140), it is possible to adjust the feed of the machine by changing the geometry of the machine. Those. at constant revolutions of the rotor 3, changing the angle of the separator 2, you can smoothly change the feed of the machine from the maximum feed in one direction to the maximum feed in the other direction.
  • the machine begins to feed the working fluid in the opposite direction, because as the volume of cameras 47 increases, they will already be connected by channels 14 to the exit windows 44, and when the volume of cameras 47 will decrease, they will be connected by channels 14 to the entrance windows 43. That is, Functionally, input windows 43 and output windows 44 are interchanged.
  • FIGS. 14-16 operates in a similar manner to the machine of FIGS. 10-13.
  • the difference is that with the help of the rail 87, through the teeth 88 and 82, the shell 89 of the separator 2 is rotated and the guide part 140 of the separator 2 is rigidly connected with it, changing its angle of inclination to the axis 6 of rotation of the rotor 3.
  • the maximum pressure drop of one stage may be greater, and the range of regulation of flow is less, for example, from zero to maximum flow.
  • the difference is that the working fluid between the channels 14 and the windows of the entrance 43 / exit 44 passes through the windows 98 in the shell 89 of the separator 2.
  • the machine of FIGS. 17-22 operates in a similar manner to the machine of FIGS. 10-13.
  • the difference lies in the method of changing the angle of inclination of the guide part 140 of the separator 2.
  • the guide part 140 of the separator 2 changes its inclination to the axis 6 of rotation of the rotor 3 due to the rotation of the shell 89 of the separator 2, made in the form of a ring 110 in a circular groove 112, the axis of rotation of the generatrix of which is inclined to the axis 6 of rotation of the rotor 3.
  • the guide part 140 of the separator 2 is also inclined to the axis of rotation of the generatrix of the sheath 89.
  • the translational movement of the rail 87 is transmitted to the rotation of the ring PO through the teeth 123 and 122.
  • a parasitic phenomenon arises - the optimal position of the input windows 43 and output 44 from The alignment to the inclination plane of the guide portion 140 of the spacer 2.
  • Care is compensated by turning the bypass sleeve 124 about the axis 6.
  • the rail 87 is also in gear engagement with the sleeve 124 through the teeth 126 and 127 or through the tooth 134 and the groove 133. This uses a different ratio.
  • the windows of the inlet 43 and the outlet 44 are located in the area of the half-shafts 10 to simplify the geometry of the sleeve 124, and the channels 14 are made inside the rotor 3, and not in the form of open grooves, as in other versions.
  • the machine of FIGS. 23-26 works similarly to the machine of FIGS. 10-13.
  • the difference lies in the method of changing the angle of inclination of the guide part 140 of the separator 2.
  • the guide part 140 of the separator 2 changes its inclination to the axis 6 of rotation of the rotor 3 due to the complex rotation of the shell 89 of the separator 2 around the center of the cavity 35.
  • the guide part 140 of the separator 2 is inclined to the axis 137 of the shell 89.
  • the translational movement of the rail 87 through the teeth 123 and 138 turns into a rotation of the shell 89, changing the angle of inclination of the guide part 140, but not turning the plane of inclination around axis 6.
  • the machine of FIG. 27 operates as follows.
  • a sphere-shaped cavity 35 of the housing 1 between the housing 1 and the rotor 3 a circular working cavity 45 is formed around the rotor 3, which the guide part 140 of the separator 2 is divided into two parts 46 of variable cross section, each of which the piston 4 divides into two working chambers 47.
  • two chambers 47 located centrally symmetrically with respect to the center of the cavity 35 increase their volume, the other two working chambers 47 decrease their volume.
  • the machine of FIG. 31 works in a similar manner to the machine of FIG. 27.
  • the difference is the ability to control the feed by changing the angle of inclination of the guide part of the separator relative to the axis 97.
  • the angle is changed due to the simultaneous rotation of the half-shafts 101 by an external control device.

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  • Rotary Pumps (AREA)

Abstract

Selon l'invention, une machine volumique rotative comprend un carter, un rotor, un séparateur doté d'une partie de guidage avec un orifice destiné au rotor, une soupape monté dans le logement du rotor et capable d'effectuer des oscillations rotatives par rapport au rotor autour de l'axe traversant l'axe de rotation du rotor sensiblement à un angle droit et possédant au moins une fente dans laquelle rentre la partie de guidage du séparateur, une cavité de travail sphérique formée autour du rotor est séparée par la partie de guidage du séparateur interagissant par l'interaction de l'orifice avec le rotor en des cavités à volume variable formant des chambres, chaque cavité étant séparée par le piston en chambres de travail. Dans la section minimale de la cavité formant chambre on a créé un passage pour le fluide de travail; en variante, le rotor peut comporter un canal permettant au fluide de travail de contourner la section minimale de la cavité formant chambre. Cela permet de modifier le caractère de la charge et de réduire l'usure du piston ainsi que de l'élément étanchéifiant de synchronisation, ce qui augmente la durée de vie de la machine. En outre, cette solution technique permet de construire des variantes réglables de cette machine.
PCT/RU2011/000031 2010-01-25 2011-01-24 Machine volumique rotative WO2011090408A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
UAA201210054A UA103721C2 (ru) 2010-01-25 2011-01-24 Объемная роторная машина
CA2788321A CA2788321A1 (fr) 2010-01-25 2011-01-24 Machine volumique rotative
US13/575,188 US20130202469A1 (en) 2010-01-25 2011-01-24 Positiv-displacement rotary mashine
CN2011800114613A CN102782254A (zh) 2010-01-25 2011-01-24 容积式旋转机构
EP11734926A EP2530241A1 (fr) 2010-01-25 2011-01-24 Machine volumique rotative

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
RU2010102009 2010-01-25
RU2010102009/06A RU2010102009A (ru) 2010-01-25 2010-01-25 Объемная роторная машина (варианты)

Publications (1)

Publication Number Publication Date
WO2011090408A1 true WO2011090408A1 (fr) 2011-07-28

Family

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PCT/RU2011/000031 WO2011090408A1 (fr) 2010-01-25 2011-01-24 Machine volumique rotative

Country Status (8)

Country Link
US (1) US20130202469A1 (fr)
EP (1) EP2530241A1 (fr)
CN (1) CN102782254A (fr)
CA (1) CA2788321A1 (fr)
EA (1) EA201100089A1 (fr)
RU (1) RU2010102009A (fr)
UA (1) UA103721C2 (fr)
WO (1) WO2011090408A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013109170A1 (fr) * 2012-01-18 2013-07-25 Didin Alexandr Vladimirovich Machine volumétrique rotative sphérique

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US826985A (en) * 1905-05-15 1906-07-24 Daniel Appel Rotary machine.
GB403914A (en) * 1933-09-02 1934-01-04 James Lewis Kempthorne Improvements in rotary motors
GB573278A (en) 1943-11-17 1945-11-14 Robert Filmer Bridgland Improvements in rotary engines, pumps, blowers or the like
DE964866C (de) * 1955-01-05 1957-05-29 Maurice Pelladeau Vorrichtung zur Anwendung als Schaltgetriebe, Pumpe, Verdichter, Zaehler, Motor, Kupplung und Bremse
GB790190A (en) * 1956-08-17 1958-02-05 Rech Etudes Prod Improvements in or relating to rotary hydraulic pumps, motors, torque converters andthe like
RU2202695C2 (ru) 2000-08-04 2003-04-20 Дидин Александр Владимирович Объемная роторная машина
RU2376478C2 (ru) 2006-06-02 2009-12-20 Александр Владимирович Дидин Роторная объемная машина
RU2382884C2 (ru) 2006-07-10 2010-02-27 Александр Владимирович Дидин Сферическая объемная роторная машина и способ работы сферической объемной роторной машины

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DE2705249A1 (de) * 1977-02-09 1978-08-10 Bosch Gmbh Robert Zahnradmaschine (pumpe oder motor)
DE4310518C1 (de) * 1993-03-31 1994-07-28 Hutter Sandra Zahnradpumpe zum Fördern eines fließfähigen Mediums
CA2174932C (fr) * 1993-10-28 2003-12-16 Alfred Parker Machine a plateau oscillant
WO2005100780A2 (fr) * 2004-04-09 2005-10-27 Hybra-Drive Systems, Llc Pompe/moteur a capacite variable
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DE102005038447B3 (de) * 2005-08-03 2007-01-25 Hüttlin, Herbert, Dr. h.c. Schwenkkolbenmaschine
RU2342537C2 (ru) * 2006-06-06 2008-12-27 Александр Владимирович Дидин Объемная роторная машина

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US826985A (en) * 1905-05-15 1906-07-24 Daniel Appel Rotary machine.
GB403914A (en) * 1933-09-02 1934-01-04 James Lewis Kempthorne Improvements in rotary motors
GB573278A (en) 1943-11-17 1945-11-14 Robert Filmer Bridgland Improvements in rotary engines, pumps, blowers or the like
DE964866C (de) * 1955-01-05 1957-05-29 Maurice Pelladeau Vorrichtung zur Anwendung als Schaltgetriebe, Pumpe, Verdichter, Zaehler, Motor, Kupplung und Bremse
GB790190A (en) * 1956-08-17 1958-02-05 Rech Etudes Prod Improvements in or relating to rotary hydraulic pumps, motors, torque converters andthe like
RU2202695C2 (ru) 2000-08-04 2003-04-20 Дидин Александр Владимирович Объемная роторная машина
RU2376478C2 (ru) 2006-06-02 2009-12-20 Александр Владимирович Дидин Роторная объемная машина
RU2382884C2 (ru) 2006-07-10 2010-02-27 Александр Владимирович Дидин Сферическая объемная роторная машина и способ работы сферической объемной роторной машины

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013109170A1 (fr) * 2012-01-18 2013-07-25 Didin Alexandr Vladimirovich Machine volumétrique rotative sphérique

Also Published As

Publication number Publication date
US20130202469A1 (en) 2013-08-08
RU2010102009A (ru) 2011-07-27
CA2788321A1 (fr) 2011-07-28
UA103721C2 (ru) 2013-11-11
EA201100089A1 (ru) 2011-08-30
CN102782254A (zh) 2012-11-14
EP2530241A1 (fr) 2012-12-05

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