VANE MACHINE HAVING STATIONARY AND ROTATING CYLINDERS WITH REDUCED CLEARANCE

1. FIELD OF APPLICATION

The invention relates to vane machines with stationary and rotating cylinder parts, from the volumetric rotating machine group.

The vane machine may be a working machine for continuous converting of working fluid energy into mechanical power, or a driving machine (pump) for continuous raising, forcing, compressing or exhausting of a fluid by mechanical power or other means, from the volumetric rotating machines group, utilising compressible or incompressible fluids as the working media.

In the International Patent Classification, it is classified as Field F—Mechanical engineering; Class F 01—Machines or engines in general; Subclass F 01 C—Rotary piston machines or engines; Group 13/00—Adaptations of machines or engines for special use, combinations of engines and devices driven thereby; Subgroup 13/02—for working hand-held pumps or the like; and 13/04—for working pumps or compressors.

2. TECHNICAL PROBLEM

The greatest problem present with volumetric machines, especially with vane volumetric machines, are the volumetric and the mechanic losses. Volume losses result from leaking of the working fluid from a higher into a lower pressure space. Mechanic losses result from friction between the machine's mutually contacting rotating and stationary parts that make parts of the working chamber. Consequence of the higher volumetric and mechanical losses is the lower volumetric and mechanical effectiveness of the machine, that is, its low total effectiveness.

The rotating parts of the cylinder have their radial and axial clearances. In axial clearance occur axial movement of the vane machine rotating parts and friction and increased wearing of the parts in contact, which decreases the mechanical effectiveness of the machine. In case of increased axial clearance of the rotating parts, these get in contact with the stationary parts, whereas the rotating parts rotate with great resistance or stop rotating, this resulting in a significant increase of mechanical losses in the vane machine.

The worn parts in contact, again, result in increased clearance between the parts and the working fluid leaking from the higher to the lower pressure spaces, which deceases the machine's volumetric effectiveness.

In the vane machine with stationary and rotating cylinders, used as a working machine, the working fluid intake and exhaust are positioned radially relative to the casing, which increases the machine's outer diameter.

The vane machine with stationary and rotating cylinders, used as a driving machine, maintain the same designed pressure at the pressurised working fluid exhaust opening, regardless of the pressure in the pressure system.

The technical problem solved by the invention is decreasing of the rotating parts clearance, decreasing the vane machine outer diameter, and using a sliding compression regulator requiring a significantly lesser power for compression.

3. STATE OF THE ART

In vane machines, the vanes are pressed against the cylinder surfaces in the working chamber by the centrifugal power, in some embodiments additionally by springs or providing the vane inner radial surface with the working-fluid pressure.

In the first vane machine embodiment, where the cylinder is stationary, the vane machine wear is proportionate to the total power pushing the vane against the cylinder surface in the working chamber and to the friction coefficient. The friction problem is being solved, among others, by selection of materials of which the vanes and the cylinder are made. The vanes may be axially moved, wherefore they lean against the working chamber stationary lateral surfaces. Due to the relative high velocities between the vane lateral surface and the working-chamber lateral surfaces, wear is present in both surfaces in contact, that is, the mechanical efficiency of the machine is deteriorated, the vane wear resulting in the working fluid leaking from the higher to the lower pressure chambers and decreasing the machine's volumetric efficiency. In this embodiment, the working chamber is charged and discharged radially, which is favourable with regard to the volumetric efficiency.

In the second vane machine embodiment, wherefore the cylinder rotates, the relative velocity at the contact between the cylinder surface, which rotates in the chamber, and the vane is decreased, this again resulting in decrease of the friction wear, which is favourable with regard to the mechanic efficiency. The weakness of this embodiment are the working-fluid axial intake and exhaust, unfavourably effecting charging and discharging of the chamber, thus worsening the volumetric efficiency.

In the third vane machine embodiment, where the cylinder comprises one stationary and two rotating cylinder parts, achieved are decreased wear of the vane surfaces in contact with the cylinder axial and radial surfaces in the vane machine working chamber, improved charging and discharging of the working chamber with the working fluid, and solved is the sealing between the vanes and the cylinder stationary part and the rotor lateral plates. This enhances the machine's volumetric efficiency and decreases losses from friction between the surfaces in contact, that is, enhances the mechanical efficiency of the machine. The weakness of this embodiment is the axial clearance of the rotating parts, which increases wear of the parts in contact, this again decreasing the machine's mechanical and volumetric efficiency. Radial intake of the working fluid into the vane machine casing increases the vane machine diameter.

The vane machines used as driving machines maintain at their pressurised working fluid exhaust always the same, given, pressure, defined by the fixed volumetric ratio. Pressure at the machine exhaust can be larger than or equal to the pressure in the pressure system taking the working fluid from the vane machine to the consumer. If pressure at the vane machine exhaust is larger than that in the pressure system, the working fluid expands and its pressure at the vane machine exhaust is decreased down to the pressure in the pressure system. The working fluid expansion and pressure decrease results in the work unnecessarily spent to increase the working fluid pressure in the vane machine.

4. ESSENCE OF THE INVENTION

The essence of the invention is the vane machine with stationary and rotating cylinder with decreased rotating cylinder parts clearance. The vane machine with rotating cylinder with decreased stationary and rotating cylinder parts clearance can be used as working and driving one.

The working vane machine has a rotating cylinder with decreased clearance of its rotating parts, placed between stationary cylinders.

The driving vane machine has a rotating cylinder with decreased clearance of its rotating parts, placed between stationary cylinders, provided with a sliding compression regulator.

The rotating cylinder with decreased rotating part clearance has bearings placed on a mutual additional ring with a raised shroud between the bearing inner rings and a spiral spring around the shroud and a fixed distancer between the bearing outer rings.

Through the stationary cylinder is made an axial canal conducting the fluid to the radial working fluid intake to the vane machine working chamber, that has decreased the machine outer diameter.

The rotating cylinders with rotating parts with decreased clearance, with regard to their shape, manufacturing precision, numbers of parts and their mutual relations, are embodied also in the following five variants:

Variant one: rotating cylinder with decreased clearance with high precision bearings, flat additional ring and fixed distancer. Variant two: rotating cylinder with decreased clearance with paired bearings, flat additional ring and fixed distancer. Variant three: rotating cylinder with decreased clearance with additional ring with raised shroud and fixed distancer. Variant four: rotating cylinder with decreased clearance with additional ring with raised shroud, fixed elements, springs and bearings. Variant five: rotating cylinder with decreased clearance, using pressurised fluid with distribution canals made through the stationary part of the rotating cylinder.

Decreasing the rotating cylinder clearance decreases wearing of the parts in contact, and this enhances the vane machine mechanical and volumetric efficiency.

The rotating cylinders with decreased clearance are used with all vane machine versions. The vane machine has one or more rotating cylinders with decreased clearance.

Using the pressurised fluid with the canals distributing the fluid through the cylinder stationary parts decreases clearance and gains better sealing between the stationary and the rotating parts of the cylinder on one side and the stationary part of the cylinder and the rotor with firmly fitted lateral plates on the other.

Using the sliding compression regulator in vane machines that are used as driving machines change the compression ratios and pressure and the vane machine exhaust, depending on the pressure in the pressure system, with significant decrease of the power required for compressing.

5. BRIEF ILLUSTRATION DESCRIPTION

FIG. 1 shows closed vane machine with stationary and rotating cylinder with decreased clearance of the rotating parts B—side view.

FIG. 2 shows the vane machine shown in the FIG. 1—perspective view.

FIG. 3 shows the vane machine shown in the FIG. 1—partial longitudinal cross-section.

FIG. 4 shows the vane machine with the first variant of the rotating cylinder with decreased clearance B1—partial longitudinal cross-section.

FIG. 5 shows the vane machine with the second variant of the rotating cylinder with decreased clearance B2—partial longitudinal cross-section.

FIG. 6 shows the vane machine with the third variant of the rotating cylinder with decreased clearance B3—partial longitudinal cross-section.

FIG. 7 shows the vane machine with the fourth variant of the rotating cylinder with decreased clearance B4—partial longitudinal cross-section.

FIG. 8 shows the rotating cylinder with decreased clearance B—side view.

FIG. 9 shows the rotating cylinder B shown in the FIG. 8—perspective view.

FIG. 10 shows the rotating cylinder B—longitudinal cross-section L-L from the FIG. 8.

FIG. 11 shows the first variant of the rotating cylinder with decreased clearance B1—side view.

FIG. 12 shows the first variant of the rotating cylinder B1 shown in the FIG. 11—perspective view.

FIG. 13 shows the first variant of the rotating cylinder B1—longitudinal cross-section J-J from the FIG. 11.

FIG. 14 shows the second variant of the rotating cylinder with decreased clearance B2—side view.

FIG. 15 shows the second variant of the rotating cylinder B2 shown in the FIG. 14—perspective view.

FIG. 16 shows the second variant of the rotating cylinder B1—longitudinal cross-section K-K from the FIG. 14.

FIG. 17 shows the third variant of the rotating cylinder with decreased clearance B3—side view.

FIG. 18 shows the third variant of the rotating cylinder B2 shown in the FIG. 17—perspective view.

FIG. 19 shows the third variant of the rotating cylinder B1—longitudinal cross-section M-M from the FIG. 17.

FIG. 20 shows the fourth variant of the rotating cylinder with decreased clearance B4—side view.

FIG. 21 shows the fourth variant of the rotating cylinder B4 shown in the FIG. 14—left lateral view.

FIG. 22 shows the fourth variant of the rotating cylinder B4—longitudinal cross-section N-N from the FIG. 20.

FIG. 23 shows the first stationary cylinder A1 with axial canal conducting the fluid to the radial working fluid intake into the machine working chamber, and the radial working fluid exhaust from the machine—side view.

FIG. 24 shows the first stationary cylinder A1 shown in the FIG. 23—perspective view.

FIG. 25 shows the first stationary cylinder A1—longitudinal cross-section H-H from the FIG. 23.

FIG. 26 shows the second stationary cylinder A2 with the radial working fluid exhaust from the machine working chamber—side view.

FIG. 27 shows the second stationary cylinder A2 shown in the FIG. 26—perspective view.

FIG. 28 shows the second stationary cylinder A2—longitudinal cross-section I-I in the FIG. 26.

FIG. 29 shows the rotor C with the lateral plates P—side view.

FIG. 30 shows the rotor C shown in the FIG. 29—side view.

FIG. 31 shows a variant of the lateral plate P1 for the rotor C with the radial opening conducting the working fluid—front view.

FIG. 32 shows a variant of the lateral plate P1 for the rotor C shown in the FIG. 31—perspective view.

FIG. 33 shows the vane E with longitudinal and transversal grooves and radial slots—perspective view.

FIG. 34 shows the vane E1 with additional shafts with bearings at its lateral side—side view.

FIG. 35 shows the vane E1 shown in the FIG. 34—front view.

FIG. 36 shows the vane E1 shown in the FIG. 34—perspective view.

FIG. 37 shows the rotor C1, having rotating shafts with bearings at the place where the vane exits the slot—side view.

FIG. 38 shows the rotor C1 shown in the FIG. 37—front view.

FIG. 39 shows the rotor C1 shown in the FIG. 37—perspective view.

FIG. 40 shows the rotating shaft with bearings for the rotor C1—perspective view.

FIG. 41 shows a variant of the lateral plate P2 for the rotor C1—side view.

FIG. 42 shows variant of the rotating lateral plate P2 for the rotor C1 shown in the FIG. 41 with slots in which moves bearing of the additional axle of the vane E1 and with openings in which firmly fixed are bearings for rotating shafts at the place where the vane exits the slot—front view.

FIG. 43 shows variant of the rotating lateral plate P2 for the rotor C1 shown in the FIG. 41—perspective view.

FIG. 44 shows casing F for vane machine with two radial working fluid exhausts—side view.

FIG. 45 shows casing F shown in the FIG. 44—front view.

FIG. 46 shows casing F shown in the FIG. 44—perspective view.

FIG. 47 shows the first cover D1 with axial working fluid exhaust—front view.

FIG. 48 shows the first cover D1 shown in the FIG. 47—perspective view.

FIG. 49 shows the first cover D1—longitudinal cross-section S-S from the FIG. 47.

FIG. 50 shows the second cover D2—front view.

FIG. 51 shows the second cover D2 shown in the FIG. 50—perspective view.

FIG. 52 shows the second cover D2—longitudinal cross-section O-O from the FIG. 50.

FIG. 53 shows variant of the cover D3 with the axial working fluid exhaust and the radial openings conducting the fluid—front view.

FIG. 54 shows variant of the cover D3 shown in the FIG. 53—perspective view.

FIG. 55 shows variant of the cover D3—longitudinal cross-section R-R from the FIG. 53.

FIG. 56 shows variant of the cover D4 with radial openings conducting the working fluid—front view.

FIG. 57 shows variant of the cover D4 shown in the FIG. 56—perspective view.

FIG. 58 shows variant of the cover D4—longitudinal cross-section P-P from the FIG. 56.

FIG. 59 shows the closed vane machine with rotating cylinder with decreased clearance B and with common axial working fluid exhaust to the first and the second stationary parts of the cylinder—side view.

FIG. 60 shows the vane machine with rotating cylinder with decreased clearance B and with common axial working fluid exhaust to the first and the second stationary parts of the cylinder—partial longitudinal cross-section.

FIG. 61 shows the closed vane machine with rotating cylinder with decreased clearance B3 and B4 and with common axial working fluid exhaust to the first, the second and the third stationary parts of the cylinder—side view.

FIG. 62 shows the vane machine with rotating cylinder with decreased clearance B3 and B4 and with common axial working fluid exhaust to the first, the second and the third stationary parts of the cylinder—partial longitudinal cross-section.

FIG. 63 shows the closed vane machine with rotating cylinder with decreased clearance B and with axial working fluid exhaust to the stationary part of the cylinder—side view.

FIG. 64 shows the vane machine with rotating cylinder with decreased clearance B and with axial opening conducting the fluid to the stationary part of the cylinder—partial longitudinal cross-section.

FIG. 65 shows the closed vane machine with rotating cylinder with decreased clearance B, B3 and B4 and with common axial working fluid intake to the first, the second and the third stationary parts of the stationary part of the cylinder—side view.

FIG. 66 shows the vane machine with rotating cylinder with decreased clearance B, B3 and B4 and with common axial working fluid intake to the first, the second and the third stationary parts of the cylinder—partial longitudinal cross-section.

FIG. 67 shows the closed vane machine with rotating cylinder with decreased clearance B and with axial working fluid intake to the stationary part of the cylinder—side view.

FIG. 68 shows the vane machine with rotating cylinder with decreased clearance B and with axial working fluid intake to the stationary part of the cylinder—partial longitudinal cross-section.

FIG. 69 shows the stationary cylinder A3 with the sliding compressor regulator G with guides on lateral sides of the radial opening conducting the fluid into and out of the vane machine working chamber—side view.

FIG. 70 shows the stationary cylinder A3 with the sliding compressor regulator G shown in the FIG. 69—front view.

FIG. 71 shows the stationary cylinder A3 with the sliding compressor regulator G—cross-section V-V from the FIG. 69.

FIG. 72 shows the stationary cylinder A3 with the sliding compressor regulator G—cross-section T-T from the FIG. 70.

FIG. 73 shows the stationary cylinder A3 with the sliding compressor regulator G—perspective view.

FIG. 74 shows the closed vane machine with rotating cylinder with decreased clearance B between the stationary cylinders A3 with the sliding compressor regulator G and working fluid intake and exhaust into and out of the vane machine working chamber, and the canal F1 for axial working fluid intake simultaneously to both radial openings through the sliding compression regulators—side view.

FIG. 75 shows the vane machine shown in the FIG. 74—partial longitudinal cross-section.

FIG. 76 shows the vane machine with the fifth variant of the rotating cylinder with decreased clearance B5—partial longitudinal cross-section.

FIG. 77 shows the longitudinal cross-section shown in the FIG. 76.

FIG. 78 shows the vane machine with the fifth variant of the rotating cylinder with decreased clearance B5—side view.

FIG. 79 shows the vane machine with the fifth variant of the rotating cylinder with decreased clearance B5—perspective view.

FIG. 80 shows the vane machine with the fifth variant of the rotating cylinder B5—longitudinal cross-section Z-Z from the FIG. 78.

FIG. 81 shows the closed vane machine with the fifth variant of the rotating cylinder with decreased clearance B5 and the stationary cylinders A4—side view.

FIG. 82 shows the vane machine shown in the FIG. 81—longitudinal cross-section.

FIG. 83 shows the stationary cylinder A4—side view.

FIG. 84 shows the stationary cylinder A4 shown in the FIG. 83—perspective view.

FIG. 85 shows the stationary cylinder A4—longitudinal cross-section U-U from the FIG. 83.

FIG. 86 shows the casing F of the vane machine with the pressurised fluid intake and exhaust canals—side view.

FIG. 87 shows the casing F shown in the FIG. 86—front view.

FIG. 88 shows the casing F shown in the FIG. 86—perspective view.

6. DETAILED DESCRIPTION OF ONE OF THE BEST INVENTION EMBODIMENTS AND ITS FUNCTIONING

The vane machine with rotating cylinder with decreased rotating parts clearance, from the volumetric rotating machines group, where the working fluid is a compressible or a incompressible fluid, according to this invention, is made as a working vane machine for continuous conversion of working fluid energy into mechanical work, or a driving machine for continuous raising, forcing, compressing or exhausting of a working fluid by mechanical power or other means.

Vane Machine

The vane machine with stationary and rotating cylinders with decreased rotating parts clearance, as shown in the FIGS. 1, 2 and 3, consists of the first stationary cylinder A1, the second stationary cylinder A2, the rotating cylinder with decreased rotating parts clearance B, the rotor C, the vanes E, the casing F and the covers D1 and D2.

The vane machine stationary and rotating cylinders are firmly fitted into the casing F.

Stationary Cylinders

The stationary cylinders are shaped as hollows rollers, in each of them rotating a rotor with vanes.

The First Stationary Cylinder—A1

The first stationary cylinder, A1, FIGS. 23, 24, 25, consists of: circular raised shroud 1, axial working fluid intake canal 2 to radial opening 5, seal 3, lateral openings 4, radial working fluid intake to the machine working chamber, and radial opening 6, opposite the working fluid exhaust 5 from the vane machine working chamber, through opening in the casing F.

The radial opening 6, at its beginning of the exhaust has a cross-section area narrowing and a gradual increase of the cross-section area towards the exit, aimed to decreasing the vane machine noise.

The vane machine with axial canal 2, conducting the fluid through the first cover D1 and the first stationary cylinder, has its outer diameter smaller than the vane machine with radial supply of the working fluid.

The Second Stationary Cylinder—A2

The second stationary cylinder, A2, FIGS. 26, 27, 28, consists of: raised shroud 12, gaskets 3, lateral openings 4, lateral working fluid exit 6 through opening in the casing F, that exits the vane machine working chamber.

The radial working fluid exhaust 6 has a cross-section area narrowing at the beginning of the exit, and a gradual increase of the cross-section area towards the exit, aimed to decreasing the vane machine noise.

The Third Stationary Cylinder—A4

The third stationary cylinder, A4, FIGS. 83, 84 and 85, consists of: raised shroud 1, gaskets 3, lateral openings 4, radial working fluid intake 5 into the vane machine working chamber, radial working fluid exhaust 6, pressurised fluid intake canals 58, and canals 59 conducting the pressurised fluid through openings in the casing F.

The radial working fluid exhaust 6 has a cross-section narrowing at the beginning of the exit, and a gradual increase of the cross-section area towards the exit, aimed to decreasing the vane machine noise.

The power of the pressurised fluid acting through the fluid conveying canals 58 in the stationary part of the cylinder B5 decrease clearance and improves sealing between the stationary and the rotating parts of the cylinder on one side, and the stationary part of the cylinder and the rotor assembly with firmly fixed lateral vanes on the other side.

The described stationary cylinder embodiments A1, A2 and A4 are fitted in all vane machines with stationary and rotating cylinders with decreased rotating parts clearance.

Rotating Cylinders

Rotating Cylinder with Decreased Rotating Parts Clearance—B

The rotating cylinder with decreased clearance B, FIGS. 8, 9 and 10, consists of: two bearings with additional ring 9 with raised shroud 10, spring 12, and fixed distancer 13.

The bearings are by their inner rings 8 pulled over the additional ring 9 and laterally leaned against the shroud 10. Between the bearing inner rings, around the shroud, there is the spring 12 that decreases the clearance. Between the bearing outer rings 7 is fitted the fixed distancer 13.

FIG. 3 shows the vane machine with the rotating cylinder with decreased clearance B, firmly fitted between the first stationary cylinder A1 and the second stationary cylinder A2, in the vane machine casing F. When the rotor C rotates, vanes E slide over inner surface 11 of the additional ring 9, thus pulling the additional ring with bearings into rotation.

The rotating cylinders with decreased clearance of its rotating parts are made in four more variants, with regard to their shape, manufacturing precision, numbers of parts and their mutual relations:

Variant One—Rotating Cylinder with Decreased Clearance—B1

The rotating cylinder with decreased clearance B1, FIGS. 11, 12 and 13, consists of: bearings, flat additional ring 16 and fixed distancer 11. This embodiment uses high precision bearings.

Two high precision bearings are pulled by their inner rings 15 over the flat additional ring 16. Between the bearing outer rings 14 is inserted the fixed distancer 13.

FIG. 4 shows the vane machine with fitted rotating cylinder with decreased clearance B1 that is firmly placed between the stationary cylinder A1 and the stationary cylinder A2 in the vane machine casing F. When the rotor C rotates, vanes E slide over inner surface 11 of the additional ring 9, thus pulling the additional ring with bearings into rotation.

Variant Two—Rotating Cylinder with Decreased Clearance—B2

The rotating cylinder with decreased clearance B2, FIGS. 14, 15 and 16, consists of: bearings, flat additional ring and fixed distancer.

Two high precision bearings are pulled by their inner rings 8 over the flat additional ring 17, and between the bearing outer rings is inserted the fixed distancer 13.

FIG. 5 shows the vane machine with fitted rotating cylinder with decreased clearance B2 that is firmly placed between the stationary cylinder A1 and the stationary cylinder A2 in the vane machine casing F. When the rotor C rotates, vanes E slide over inner surface 11 of the additional ring 17, thus pulling the additional ring with bearings into rotation.

Variant Three—Rotating Cylinder with Decreased Clearance—B3

The rotating cylinder with decreased clearance B3, FIGS. 17, 18 and 19, consists of: bearings, additional ring 18 with raised shroud 19 and fixed distancer 13.

Two high precision bearings are pulled by their inner rings 8 over the flat additional ring 18, on both sides of the shroud 19, and between the bearing outer rings 7 inserted is the fixed distancer 13.

FIG. 6 shows the vane machine with fitted rotating cylinder with decreased clearance B3 that is firmly placed between the stationary cylinder A1 and the stationary cylinder A2 in the vane machine casing F. When the rotor C rotates, vanes E slide over inner surface 11 of the additional ring 18, thus pulling the additional ring with bearings into rotation.

Variant Four—Rotating Cylinder with Decreased Clearance—B4

The rotating cylinder with decreased clearance B4, FIGS. 20, 21 and 22, consists of: bearings, additional ring 20 with raised shroud 21. On the fixed distancer 22 rotates bearing 23 with spring 20 with shroud 21. On the lateral holder 24 rotates bearing 25 with spring, on the lateral holder 26 rotates bearing 27 with spring. The bearings lean with the outer rings against front and lateral surfaces of the shroud 21 on the additional ring 20, thereby decreasing radial and axial clearances of the cylinder rotating parts.

FIG. 7 shows the vane machine with fitted rotating cylinder with decreased clearance B4 that is firmly placed between the stationary cylinder A1 and the stationary cylinder A2 in the vane machine casing F.

When the rotor C rotates, vanes E slide over inner surface 11 of the additional ring 20, thus pulling the additional ring with bearings into rotation.

Variant Five—Rotating Cylinder with Decreased Clearance—B5

The rotating cylinder with decreased clearance B5, FIGS. 78, 79 and 80, consists of: rotating part 54 of the rotating cylinder B5 and stationary part 55 of the rotating cylinder B5 with pressurised fluid intake canal 56 on the stationary part 55 and pressurised fluid exhaust canal 57 out on the stationary part 55. The power of the pressurised fluid acting through the fluid canals 56 taking the fluid to the rotating part 54 improves axial and radial guiding of the rotating part 54 and decreases radial and axial clearance of the cylinder rotating parts.

FIG. 77 shows the vane machine with fitted rotating cylinder with decreased clearance B5 that is firmly placed between the stationary cylinder A1 and the stationary cylinder A2 in the vane machine casing F.

When the rotor C rotates, vanes E slide over inner surface of the rotating part 54, thus pulling it into rotation.

Bearings in rotating cylinders may also be sliding ones. Additional rings width may exceed the total width of the bearings.

More complex versions of rotating cylinders are embodied in several different combinations aimed to decreasing the clearance, where all combinations of distribution and sizes of elements are possible, depending on the machine's required technical characteristics. Other mechanical solutions known in the present state of art, not mentioned here, and aimed to decreasing clearance of the cylinder rotating parts, are possible as well.

Rotors

As shown in the FIGS. 29 and 30, rotor C has shaft 28, body 29 with longitudinal slots 30 and lateral plates P. The vane machine lateral plates are firmly pulled over the shaft and leaned against the rotor body, so that they close the cylinder chamber with their lateral sides. The lateral plate, in the P1 variant, as shown in the FIGS. 31 and 32, have radial canals 31 conducting the working fluid. The rotor has one or more longitudinal slots 30 for vanes E. The rotor rotates in the cylinder working chamber together with the lateral plates P and the vanes E. The rotor rotates in bearings, that may be rolling or sliding. The bearings are firmly fitted in openings 37 of covers D1 and D2.

The slots in the rotor body may also be made to allow the vanes to move under an angle closed by the vane surface and the radial direction of the rotor. The rotor edges are slanted at the point where vanes exit the slots, in order to decrease the vane lateral wear.

FIGS. 37, 38 and 39 show the rotor variant C1 that, at the point where vanes exit the slots, has slots for the rotating shafts 48. The rotating shafts are here to decrease mechanical losses and vane lateral wear, and to enable machine operation without lubrication. The rotating shafts, FIG. 40, at their ends have bearings 49. As shown in the FIGS. 41, 42 and 43, the rotor lateral plates, of the variant P2, have openings 50 wherein are firmly fitted bearings 49 of the rotating shafts 48. The P2 plates also have slots 51 wherein move the bearings 53 on additional shafts 52 of the variant E1 vane.

The rotor body may also be longitudinally grooved over its outer surface with, this resulting in labyrinth sealing. The rotor body, between the vane slots, may have one or more axial openings to decrease the rotor mass.

Vanes

Vanes are made with or without grooves. The invention example described here is a vane machine that in its rotor has grooved vanes, known as the labyrinth seal.

The vanes E, FIG. 33, have body 32 on which are radial slots 33 that take the pressurised working fluid below the vane into the machine working chamber. In the middle part of the upper surface of the vane there are flat surfaces 34, whereas at its ends are recessed axial grooves 35, producing labyrinth seal. On both narrower lateral surfaces there are radial grooves 36, producing labyrinth seal by the entire length. The vanes are inserted into the slots 30 in the rotor body. The vane length equals the sum of lengths of stationary and rotating cylinder parts.

Making vanes of three or more parts enables more efficient decreasing of the vane lateral wear and achieving better seal.

When the rotor rotates, the vane flat surfaces 34 slide over the additional ring inner surfaces, thus pulling the rotating cylinder bearings into rotation.

FIGS. 34, 35 and 26 show the vane variant E1, having additional shafts 52 at lower parts of the lateral planes: to the additional shafts firmly are fitted bearings 53. Bearings move through slots 51 made in the rotor lateral plane variant P2. This decreases mechanical losses since there is no vane lateral wear and operation without lubrication is enabled.

Vane Machine Casing

FIGS. 44, 45 and 46 show the vane machine casing F, in which are fitted stationary cylinders, rotating cylinders with decreased rotating parts clearance, and rotor with vanes and covers.

FIGS. 59, 61, 63, 65, 67 and 74 show version F1 of the axial working fluid intake to all stationary cylinders. The axial intake is made at the casing F outer surface.

FIGS. 76, 77, 86, 87 and 88 show the version with an opening taking the pressurised working fluid intakes and exhausts into and out of the cylinder rotating part, whereas FIGS. 81 and 82 show the version with an opening taking the pressurised working fluid into and out of the cylinder rotating and stationary parts.

Covers

The vane machine has cover D1 and cover D2, between which are situated stationary and rotating parts of the cylinder with decreased rotating parts clearance.

The cover D1 is fitted firmly into the first stationary cylinder, and the cover D2 into the second stationary cylinder, so that they laterally lean against the stationary cylinders shroud 1.

Cover D1

The cover D1, FIGS. 47, 48 and 49, at its outer surface has axial working fluid exhaust canal 41. The axial canal 41 leans against the axial canal 2 in the first stationary cylinder A1. Through the axial canals the working fluid flows to the radial opening 5 and, through it, into the vane machine working chamber. The opening 38 in the cover is made eccentric, relative to the axis 39, and in it enters the lateral plate P of the rotor C. FIGS. 53, 54 and 55 show the cover variant D3 with axial canal 41 and radial openings 43 conducting the working fluid.

The outer diameter of vane machine with the working fluid axial intake through the cover D1 and the first stationary cylinder A1 is lesser than that of the vane machine with radial opening 5 taking the working fluid in through the casing F and the first stationary cylinder.

The cover and the first stationary cylinder with axial canal are applied to all versions of vane machine with stationary and rotating cylinder parts.

Cover D2

FIGS. 50, 51 and 52 show cover D2, and FIGS. 56, 57 and 58 the cover variant D4 with radial openings 43 conducting the working fluid.

FIG. 59 shows a closed vane machine, and FIG. 60 a partial cross-section of the same vane machine that, on the casing F, has canal F1 axially taking the working fluid simultaneously to radial openings through the first and the second stationary cylinders into the vane machine working chamber.

FIG. 61 shows a closed vane machine, and FIG. 62 a partial cross-section of the same vane machine that, on the casing F, has canal F1 axially taking the working fluid simultaneously to radial openings through the first, the middle, and the second stationary cylinders into the vane machine working chamber.

FIGS. 63 to 68 show some of the numerous possible more complex vane machine embodiments, with different numbers, shapes and mutual positions of stationary and rotating parts of cylinders with decreased clearance between the rotating parts.

Driving Vane Machine

Driving vane machine consists of rotating cylinder with decreased clearance of rotating parts B, stationary cylinder A3 with sliding compression regulator G, rotor C, vanes E, casing F and covers D1 and D2. The stationary cylinder A3 with the sliding compression regulator and the driving vane machine rotating cylinder are firmly fitted in the casing F.

The sliding compression regulator enables changing the compression ratios and pressure at the vane machine exhaust, depending on pressure in the pressure system. Pressure at the machine exhaust may be larger than or equal to pressure in the pressure system taking the working fluid from the vane machine to the consumer. If pressure at the vane machine exhaust is larger that that in the pressure system, the working fluid expands and its pressure decreases at the machine exhaust down to the pressure in the pressure system. The working fluid expansion and pressure decrease results in the loss of the work spent to increase the working fluid pressure in the vane machine, with significant increase of the working fluid flow. In driving vane machines are also fitted rotating cylinders with decreased rotating parts clearance made by the variants B1, B2, B3, B4 and B5.

Stationary Cylinder A3 with Sliding Compression Regulator G

The stationary cylinder A3, FIGS. 69, 70, 71, 72 and 73, consists of body 44, slots 45, working fluid intake opening 46, sliding compression regulator G, and sliding regulator guide 47.

FIG. 74 shows a closed driving vane machine with stationary cylinder A3 with fitted sliding compression regulator G and axial canal F1 taking the working fluid out, and FIG. 75 shows a partial cross-section of the driving vane machine shown in the FIG. 74.

Moving the sliding compression regulator changes size of the opening 46, that is, the compression relations of the driving vane machine. The sliding compression regulator movements are controlled automatically. The sliding compression regulator movements and control are achieved by any of the presently known mechanical solutions that are not stated here. More complex versions of the sliding compression regulator consist of several different combinations of shapes and guiding of the sliding compression regulator, where all combinations of distribution and sizes of elements are possible, depending on the required machine technical characteristics.

Parts of the stationary cylinders in contact with rotating parts of the cylinder and the rotor body have seals 3 and linings made of materials of the hardness lesser than that of the basic material of the parts in contact by at least 25 HRB, which seals or linings enhance sealing at the places of contact of the cylinder stationary and rotating parts and at the parts rotating at different speeds.

Functioning of the Invention

A closed vane machine appearance is shown in the FIG. 1, side view, FIG. 2, perspective view, and FIG. 3, partial longitudinal cross-section of the FIG. 1.

The vane machine working chamber is enclosed with inner surfaces of the first stationary cylinder A1, the second stationary cylinder A2, the rotating cylinder with enhanced sealing of rotating parts B, the rotor C and the vanes E.

Depending on the number of vanes, the working chamber is divided into two or more parts.

The vane machine works by creating tangential power from difference of pressures on the rotor vanes. The tangential power appears on the rotor shaft as the torque moment that, with the operating number of rotor revolutions, produces power of the machine. Power in working machines is converted into available mechanical work, whereas driving machines utilise the available power to change the working fluid pressure at a given flow.

Rotation of the rotor creates periodical charging and discharging of the working chamber, wherefore, depending on the vane machine purpose, the pressure in the working chamber is increased or decreased from the intake to the exhaust.

Vane machine is put in motion by taking fluid into the working chamber through axial canal 4 of cover D1, axial canal 2 and radial opening 5 of the first stationary cylinder A1. Here the working fluid in working machine, due to the pressure difference, makes the rotor to rotate, whereas in driving machines the power available at the rotor is used to change the working fluid pressure at a given flow. The fluid in the space between two vanes exits the working chamber through radial opening 6 of the first stationary cylinder A1 and the second stationary cylinder A2, and the cycle is repeated. In working machines, the radial opening 5, conducting fluid into the machine working chamber, is lesser than or equal to the radial opening 6, taking the fluid out. In driving machines, the radial opening 5, conducting fluid into the machine working chamber, is larger than or equal to the radial opening 6, taking the fluid out. Other combinations of widths, aimed to decreasing the volumetric losses, are possible as well.

Rotation of the rotor creates centrifugal power pushing the vanes E out of the slots 30, this creating friction between the flat parts of the vanes 34 and the inner surface 11 of the additional ring 9 of the rotating cylinder B, that pulls the vanes into rotation.

The velocity of sliding between the vanes and the additional rings at the surfaces in contact is the difference between the current peripheral velocity of the vane outer edge and the current peripheral velocity resulting from the additional ring rotation. In this machine, this velocity depends on the number of the vanes. With just one vane in the rotor the velocity is zero, and with more of them the maximum sliding velocity is the difference between the velocities of vanes with the maximum and the minimum peripheral velocities, depending on the current additional ring rotation speed.

The vanes may be moved axially, where they lean against the lateral plates P of the rotor C. The rotating lateral plates are firmly fitted to the rotor, laterally closing the working chamber, and rotate together with and at the same peripheral velocity as the rotor. This results in the minimum relative sliding velocity between the vane lateral edges and the plates, this again resulting in lesser wear due to vane and plates wearing and, thereby, increased mechanic efficiency. The relative velocity between the vane lateral edges and the working chamber plates results only from the vane radial movement. Between the vanes and the stationary cylinder inner surfaces there is clearance and, therefore, no mutual contact, which avoids friction wear at that place. Decreasing the friction losses increases mechanical efficiency of the machine.

Edges of the rotor C, at the point of the vane exiting the slot 30, are angled, to decrease the vane lateral wear. Pressure of the vane against the additional ring 9 produces seal at that place. The pressure is additionally increased by spring placed in the canal below the vane or by taking pressurised working fluid to the vane inner radial surface, that produces additional lateral power. The pressure may, if required, be further decreased by means of the radial slots 33 in the vane body, which slots take the pressurised working fluid below the vane and into the machine working chamber. Where an opening is made through the rotating plate, connecting the space below the vane with the working fluid exhaust from the working chamber, the pressure under the vane equals the exhaust pressure.

In this case, where vane with slots is used to remove the pressure building below the vane, the vanes are pressed against the additional ring of the bearing inner ring only by the centrifugal power, which decreases the vane pressure power against the bearing additional ring and, thereby, the vane friction and wear. Where the vane is made of three or more parts, the vane lateral wear can be decreased more efficiently and better seal can be achieved.

Normally, parts of the vane machine are made by various techniques of particle removal. In cases where used materials are hard for mechanic treatment, and resistant to chemicals, abrasion and cavitation, or where the time required for production from standard materials used in vane machine production is shortened by applying technologies of particle removal, parts are made by casting technology that enables minimum application of particle removal techniques as the final stage of production.

The rotating cylinder with decreased rotating parts clearance B has rolling and sliding bearings with radial and axial clearances. The essential problem that is solved by this invention is a decreased clearance of the rotating cylinder parts, that reduces wear of parts in contact by axial movement of the elements, and thereby enhances the entire machine mechanical efficiency. In cases of increased axial clearance of rotating parts, the rotating cylinder parts make contact with cylinder stationary parts, and the rotating parts rotate with a large resistance or stop rotating. This results in a significant increase of mechanical losses within the vane machine or its complete stoppage. Decreasing of clearance between the vane machine elements, due to the decreased wear of the parts in contact, decreases flow from working fluid higher pressure to lower pressure spaces and, thereby, enhances the machine volumetric efficiency. Decreasing of clearance of rotating parts, by this invention, is solved in several ways: by springs decreasing the rotating parts clearance, high precision bearings with decreased radial and axial clearance, paired bearings with fixed distance between the bearings to decrease the rotating parts clearance, and by fixed elements, springs and bearings for axial and radial decrease of rotating parts clearance, and by applying pressurised fluid with canals distributing the fluid through the stationary part of the cylinder rotating part for axial and radial guiding of the rotating part and decreasing of radial and axial clearances of the rotating cylinder parts. Application of pressurised fluid with canals distributing the fluid through the stationary cylinder parts decreases clearance and achieves more efficient seal between the cylinder stationary and rotating parts, as well as between the cylinder stationary part and the rotor assembly with firmly fitted lateral plates.

Depending on the required degree of precision of decreasing the rotating parts clearance, possible are all mutual combinations of distribution and sizes of elements, in line with the given machine technical characteristics. Application of other presently known mechanical solutions, not stated in here, and aimed to decreasing the rotating parts clearance are possible as well. Axial decreasing the rotating parts clearance is applied in all vane machine versions containing rotating parts.

The issue of the vane machine volumetric efficiency of is partly solved by utilising as much as possible the space available in the stationary part of the working chamber cylindrical wall for the working fluid radial intakes and exhausts in and from the machine working chamber. Structural solution enables additional increasing the working fluid intake and exhaust canal cross-sections, wherefore the canals are shaped as a full rectangular opening, which achieves their largest possible area. Utilisation of the largest possible cross-section of the working fluid intake and exhaust canals improve conditions for charging and discharging the vane machine working chamber. Taking the working fluid into the vane machine is improved by placing the stationary cylinders at the end of the cylinders, with the rotating cylinders between them. The rotating cylinders make rolling or sliding bearings mutually connected by the additional ring. Between the first stationary cylinder at the machine intake and the casing F there is the axial canal taking the working fluid to the radial opening 5, the machine working chamber intake, and the radial opening 6, the machine working chamber exhaust. The first stationary cylinder has working fluid intakes and exhausts in and from the machine working chamber, whereas the second cylinder, at the machine exit, only has the radial opening 6 to discharge the working fluid from the working chamber. The radial working fluid exhaust, at its beginning has a cross-section area narrowing and a gradual increase of the cross-section area towards the exit, aimed to decreasing the vane machine noise. This achieves a better volumetric efficiency of the machine and the decreased vane machine total diameter.

In the present state of art there are vane machines of several different constructions and functioning, applied as driving machines utilising the power available at the vane machine entrance to increase the fluid pressure with a given flow. The compression ratio in vane machines with several vanes and applied as driving machines is determined by the structurally set vane machine dimensions: rotor radius, cylinder radius and the opening angle of the pressurised working fluid exhaust. They are characterised by always having the same given pressure at the pressurised fluid exit from the vane machine, regardless of the pressure in the pressure system taking the working fluid out from the vane machine to the consumer. Pressure in the pressure system depends on consumption by the consumers connected to the pressure system and leakages within the pressure system, and it is lesser than or equal to the pressure at the exit of the working fluid from the vane machine.

As long as there is a difference of the working fluid pressures between the vane machine exit and the pressure system, at the vane machine exit into the pressure system occur working fluid explosions and decrease of the working fluid pressure at the vane machine exit down to the pressure in the pressure system. Decreasing the working fluid pressure from the pressure at the vane machine exit down to the pressure in the pressure system nullifies the work used to increase the working fluid pressure, which means there is work unnecessarily spent to increase the working fluid pressure.

By using the compression regulator G, by which the pressure at a working vane machine exit can be changed in accordance with the pressure in the pressure system, which is the highest pressure in the vane machine, enables supplying with working fluid of a pressure minimally higher than that in the pressure system, with a significant increase of the working fluid flow.

In the structure of the vane machine with stationary cylinders and rotating cylinder with decreased rotating parts clearance, with the working fluid intake and exhaust openings large enough, the issue of the unnecessary work spent in increasing the working fluid pressure is solved by making the pressurised working fluid exit from the vane machine narrower than the working fluid intake. The working fluid intake radial opening is of a larger diameter because it is entered by a larger volume of the working fluid of a lesser pressure.

Vane machines applied as driving machines, at their pressurised working fluid exhausts always have the same and in advance given pressure, defined by the fixed volume ratio. Pressure at the machine exhaust may be larger than or equal to the pressure in the pressure system that takes the working fluid from the vane machine to the consumer. If the pressure at the driving vane machine exhaust equals the pressure in the pressure system, the driving vane machine works with the maximum rated pressure, in which case the compression sliding regulator G does not cover the working fluid intake opening 5. If pressure at the driving vane machine exhaust is larger that the pressure in the pressure system, the vane machine works under a pressure lesser than the maximum rated pressure, and the compression sliding regulator partly covers the working fluid intake opening 5. The working fluid intake opening 5 is designed to have its cross-section large enough that, when it is partly covered by the compression sliding regulator, this does not obstruct its normal working cycle, that is, when partly covered it works without damping that would decrease supply of the fluid into the vane machine. The compression sliding regulator enables supplying with the working fluid of a pressure minimally higher than that in the pressure system, with significant decrease of the power required for compressing.

Vane machines applied as driving machines have rotating plates P1 with radial openings 31 conducting the working fluid to the covers D. The covers are connected by canal with the radial opening 5 in the stationary parts of the cylinder A, taking the fluid into the machine working chamber. The rotating plates P at the end of the ring 17 for vanes at the rotor C have radial openings that enable communication between the space below the vane E in the vane opening in the rotor and the intake canal 5, thus maintaining a constant intake pressure of the working fluid below the vane. In this case, the vanes come out of the rotor only powered by the centrifugal power. The vanes are to be rectangular, with no radius or angling in their lower parts, because when working a vane by its entire length always leans against the lateral sides of the rotor slot, thus creating seal and preventing communication of the working fluid with the area below the vane.

Description of Vane Machine with Several Stationary and Rotating Cylinder Parts

FIGS. 63 to 68 show some of the numerous possible vane machine embodiments with various numbers, shapes and mutual positioning of stationary and rotating parts of the rotating cylinder with decreased rotating parts clearance.

Stationary and rotating cylinders may be distributed in the casing in several other manners, depending on the given technical characteristics of the machine. In the presented embodiments, the lateral plates P, rotating jointly with the rotor C, are placed in eccentric openings in the covers D or in the stationary cylinders.

Distribution of rotating parts of the cylinder B also determines positions of flat parts of the vane E without the grooves 34.

More complex versions of the vane machine have more stationary and rotating cylinder parts, with all possible combinations of mutual distribution and sizes of stationary and rotating parts. Distribution of stationary and rotating cylinder parts in more complex forms of vane machines may demand different shapes and distributions of other parts housed in such vane machine casing.

More complex versions of the vane machine may have several vane machines on the same rotor, aimed to increasing the total power, where all combinations of mutual distribution and sizes of vane machines are possible.

The above mentioned more complex vane machine versions do not alter the spirit of the invention presented in the basic embodiment of the vane machine with stationary and rotating cylinder parts with decreased rotating parts clearance.

7. INVENTION APPLICATION

The vane machine with stationary and rotating cylinder parts with decreased rotating parts clearance may be used as a working or a driving machine. As a working machine, it converts the initially available energy of a compressible or incompressible working fluid into mechanical work; whereas as a driving machine it converts mechanical work, at a given flow, into change of pressure of a compressible or incompressible working fluid.

As a powering or a driving machine with compressible fluid it is applied: as a pneumatic pump, in mechanisation of various technological processes, as starter of large diesel engines, compressor, pump, vacuum pump, internal combustion engine, compressor for supercharging of working fluid in internal combustion engines.

As a working or powering machine with non-compressible fluid it is applied: in power, motion or momentum transferring systems in building machines, hydraulic cranes, ship hydraulics, hydro powering of processing machines, and at controlling regulation or protection in hydraulic systems for automation of working processes.

As a pump or hydro engine it has two main fields of application, with regard to the working fluid. When the working fluid is a mineral oil, the self-lubrication decreases friction and, thereby, wear of the machine vanes and casing, which is the most significant weakness in vane machines. This is being applied in power, motion and momentum transferring systems in building machines, hydraulic cranes, ship hydraulics, hydro powering of processing machines, and at controlling regulation or protection in hydraulic systems for automation of working processes. Hydraulic vane machines are able to change the rotation velocity in a wide scope. The lesser inertia powers of its moving parts makes the machine often starting and the starting and stopping processes easier. Applying of working fluid that have no lubricating properties, the vane and casing wear issue remains the main vane engine or pump weakness.

BRIEF DESCRIPTION OF THE ALPHABETIC AND NUMERIC MARKS USED IN THE INVENTION DESCRIPTION AND ILLUSTRATIONS
Stationary Cylinders

A1—first stationary cylinder with axial canal conducting the working fluid to the fluid radial

intake into the machine working chamber and with fluid radial exhaust from of the machine

working chamber

A2—second stationary cylinder with radial exhaust from the machine working chamber

A3—third stationary cylinder with canals distributing the pressurised fluid

1—shroud

2—axial working fluid intake canal

3—seal in the shroud's lateral plate

4—lateral openings of the cylinder stationary parts

5—working fluid radial intake

6—working fluid radial exhaust

58—pressurised fluid intake canals

59—pressurised fluid exhaust canals

Rotating Cylinders

B—rotating cylinder with bearings firmly fitted to the common additional ring with shroud between the bearing inner rings and spiral spring around the shroud and the fixed distancer between the bearing outer rings

B1—rotating cylinder with high precision bearings, flat additional ring and fixed distancer—variant one

B2—rotating cylinder with paired bearings, flat additional ring and fixed distance—variant two

B3—rotating cylinder with additional shroud and fixed distancer—variant three

B4—rotating cylinder with additional ring with shroud, fixed elements, springs and bearings—variant four

B5—rotating cylinder with clearance decreased by using pressurised fluid with distributing canals made through the stationary part of the rotating cylinder—variant five

7—bearing outer ring

8—bearing inner ring

9—additional ring with shroud

10—shroud on additional ring

11—additional ring working surface

12—spring around the additional ring shroud

13—fixed distancer between the bearing outer rings

14—high precision bearings outer ring

15—high precision bearing inner ring

16—additional ring in the first variant of the rotating cylinder B1

17—additional ring in the second variant of the rotating cylinder B2

18—additional ring in the third variant of the rotating cylinder B3

19—raised shroud on the additional ring 18

20—additional ring in the fourth variant of the rotating cylinder B4

21—raised shroud on the additional ring 20

22—fixed outer distancer

23—bearing with spring on the fixed distancer 22

24—side holder

25—bearing with spring on the fixed distancer 24

26—side holder

27—bearing with spring on the fixed distancer 26

54—rotating part of the rotating cylinder B5

55—stationary part of the rotating cylinder B5

56—pressurised fluid inflow canals on stationary part of rotating cylinder B5

57—pressurised fluid exhaust canal on stationary part of rotating cylinder B5

Rotor

C—rotor with lateral plates P

28—rotor shaft

29—rotor body

30—vane slots

P—lateral plates on rotor

P1—lateral plates for rotor with radial openings conducting the working fluid

31—radial openings conducting the working fluid

C1—rotor variant with rotating shafts

48—rotating shafts at the exit of the vane from its slot in the rotor variant C1

49—bearings on rotating shafts

P2—lateral plate variant in the rotor variant C1

50—openings in lateral plate P2 in which are firmly fitted bearings 49

51—slots in the lateral plate P2 in which move bearings 53 on additional shafts in the vane variant E1

Vanes

E—vane with radial openings

32—vane body

33—radial slot taking the working material away

34—flat parts of vanes without grooves

35—axial grooves

36—radial grooves

E1—vane variant with additional shafts

52—additional shaft at lateral side of the vane variant E1

53—bearing on additional shaft

Covers

D1—cover with axial canal

37—eccentric openings in the rotor bearing cover

38—openings in the rotor lateral plate cover

39—cover axial axis

40—eccentric opening axial axis

41—axial canal taking the fluid in

D2—cover without axial canal

D3—cover with axial opening and radial openings for working fluid

43—radial openings conducting the working fluid

D4—cover without axial opening with radial openings taking the fluid in

Casing

F—vane machine casing

F1—canal for axial taking the working fluid simultaneously to radial openings through the first and the second stationary cylinders into the machine working chamber

Stationary Cylinder with Sliding Compression Regulator

A3—stationary cylinder with sliding compression regulator

G—sliding compression regulator

44—compression regulator body

45—slots for sliding of the sliding compression regulator guide

46—opening that passes the working fluid into and out of the vane machine working chamber

47—guides opening and closing the opening that passes the working fluid

VANE MACHINE HAVING STATIONARY AND ROTATING CYLINDERS WITH REDUCED CLEARANCE

Information

Publication Number

Date Filed

Date Published

Inventors

CPC

International Classifications

Abstract

Description

Claims

Priority Claims (1)

PCT Information