EP2467580A2

EP2467580A2 - Vane machine with enhanced sealing among stationary and rotating cylinder parts

Info

Publication number: EP2467580A2
Application number: EP10763416A
Authority: EP
Inventors: Nebojsa Boskovic; Branimir Matijasevic
Original assignee: Individual
Current assignee: Individual
Priority date: 2009-08-20
Filing date: 2010-08-13
Publication date: 2012-06-27
Also published as: WO2011021055A2; HRP20090445A2; WO2011021055A3; HRPK20090445B3

Abstract

Vane -machine comprising: cylinder stationary part (A), cylinder rotating parts (B), rotor (C), covers (D), and vanes with grooves (F), and sealing among the cylinder stationary and rotating parts. The enhanced sealing among the cylinder stationary and rotating parts is achieved by fitting, on the parts in contact o the cylinder stationary and rotating parts, of inserts or linings made from a material of the hardness lesser by at least HRB 25 than the hardness of the basic material from which the parts in contact are made, where all combinations of distribution of inserts or linings are possible. The lateral plates that rotate in eccentric openings of the cylinder stationary parts or in eccentric openings of the covers at the places of contact with the vanes have protrusions slots or grooves to guide the lateral inserts (26) with the radial labyrinth- sealing grooves, which lateral inserts lean laterally against the vane.

Description

VANE MACHINE WITH ENHANCED SEALING

AMONG STATIONARY AND ROTATING CYLINDER PARTS

INVENTION DESCRIPTION

1. FIELD OF APPLICATION

The invention relates to vane machine with enhanced sealing among stationary and rotating cylinder parts.

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

In the International Patent Classification, it is classified as the 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 driving hand-held tools or the like; and 13/04 - for driving 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 media from a higher pressure space into the lower pressure space. Volumetric losses also appear due to leakage of the fluid from higher- pressure space of the working chambers into lower-pressure space of the working chambers. 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 technical problem solved by the invention is an enhanced sealing among the stationary and the rotating cylinder parts, resulting in a better volumetric utilisation of the machine and reduced wear of the parts in contact, wherefrom an enhanced mechanical durability of the machine.

3. STATE OF THE ART

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

Wear of the stationary-cylinder vane machines is proportionate to the total force 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. In this embodiment, the working chamber may be charged and discharged radially, which is favourable with regard to the volumetric efficiency.

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

Similar to the first embodiment, the vanes may be axially moved, wherefore they lean against the chamber stationary lateral surfaces. Due to the relatively large velocities between the vane lateral surface and the working-chamber lateral surfaces, wear is present in both surfaces in contact.

In the third vane-machine embodiment, in the basic vane-machine version the cylinder comprises one stationary and two rotating cylinder parts. More complex vane-machine versions may contain several cylinder stationary and rotating parts, where all distribution and size combinations are possible, depending on the required machine characteristics. This embodiment achieves lesser wear of the vane surfaces in contact with the cylinder axial and radial walls in the wane-machine working chamber, as well as an enhanced charging and discharging of the working space with the working medium, and solves the problem of sealing between the vanes and the cylinder stationary part and the rotor lateral plates. This enhances the volumetric efficiency and decreases the losses from friction between the surfaces in contact, that is, enhances the mechanical efficiency of the machine. The weakness of this embodiment is leaking of the fluid from the working part of the cylinder between the stationary and the rotating cylinder parts, wear at the places of contact between the stationary and the rotating cylinder parts, and impossibility to substitute the vane lateral wear.

4. DISCLOSURE OF THE INVENTION

The essence of the invention is the vane-machine with enhanced sealing among the cylinder stationary and rotating parts, of enhanced machine volumetric efficiency. Furthermore, the losses du to friction between the contacting surfaces of the stationary and the rotating cylinder parts are decreased, this enabling more efficient substitution of vane wear and an enhanced machine mechanical durability.

The sealing between the stationary and the rotating cylinder parts is enhanced by fitting on the parts in contact of the cylinder stationary and rotating parts, of inserts or linings or the parts in contact are made from a material of the hardness lesser by at least HRB 25 than the hardness of the basic material from which the parts in contact are made, where all combinations of distribution of inserts or linings are possible. The lateral plates that rotate in eccentric openings of the cylinder stationary parts or in eccentric openings of the covers at the places of contacts with the vanes have protrusions, slots or openings for guiding the lateral inserts with radial labyrinth- sealing grooves leaning laterally against the vane.

5. ILLUSTRATION DESCRIPTIONS

Figure 1 shows vane machine - front view.

Figure 2 shows closed vane machine - side view. Figure 3 shows vane machine - cross-section A1-A1 in the Figure 1, showing all the places requiring air sealing.

Figure 4 shows closed vane machine - front view.

Figure 5 shows closed vane machine - side view.

Figure 6 shows closed vane machine - back view.

Figure 7 shows vane machine - cross-section B1-B1 in the Figure 5.

Figure 8 shows the vane machine - 3D view, isometric.

Figure 9 shows the rotating part of the cylinder B with a one-piece additional ring and an insert made from a different material - front view.

Figure 10 shows the rotating part of the cylinder B with a one-piece additional ring and an insert made from a different material - longitudinal cross-section C1-C1 in the Figure 9.

Figure 11 shows the rotating part of the cylinder B with a one-piece additional ring and an insert made from a different material - 3D view, isometric.

Figure 12 shows the rotating part of the cylinder B with a one-piece additional ring and lining made from a different material - front view.

Figure 13 shows the rotating part of the cylinder B with a one-piece additional ring and lining made from a different material - longitudinal cross-section D1-D1 in the Figure 12.

Figure 14 shows the rotating part of the cylinder B with a one-piece additional ring and lining made from a different material - 3D view, isometric.

Figure 15 shows the rotating part of the cylinder B with a two-piece additional ring and an insert made from a different material - front view.

Figure 16 shows the rotating part of the cylinder B with a two-piece additional ring and an insert made from a different material - longitudinal cross-section E-E in the Figure 15.

Figure 17 shows the rotating part of the cylinder B with a two-piece additional ring and an insert made from a different material - 3D view, isometric.

Figure 15a shows the rotating part of the cylinder B with a one-piece additional ring and an insert made from a different material - front view.

Figure 16a shows the rotating part of the cylinder B with a one-piece additional ring and an insert made from a different material - longitudinal cross-section E1-E1 in the Figure 15a. Figure 17a shows the rotating part of the cylinder B with a one-piece additional ring and an insert made from a different material - 3D view, isometric.

Figure 18 shows the rotating part of the cylinder B with a two-piece additional ring and lining made from a different material - front view.

Figure 19 shows the rotating part of the cylinder B with a two-piece additional ring and lining made from a different material - longitudinal cross-section F1-F1 in the Figure 18.

Figure 20 shows the rotating part of the cylinder B with a two-piece additional ring and lining made from a different material - 3D view, isometric.

Figure 18a shows the rotating part of the cylinder B with a one-piece additional ring and lining made from a different material - front view.

Figure 19a shows the rotating part of the cylinder B with a one-piece additional ring and lining made from a different material - longitudinal cross-section F1-F1 in the Figure 18a.

Figure 20a shows the rotating part of the cylinder B with a one-piece additional ring and lining made from a different material - 3D view, isometric.

Figure 21 shows the stationary part of the cylinder A - front view.

Figure 22 shows the stationary part of the cylinder A - side view.

Figure 23 shows the stationary part of the cylinder A - back view.

Figure 24 shows the stationary part of the cylinder A - 3D view, isometric.

Figure 25 shows the stationary part of the cylinder A - with an insert made from a different material.

Figure 26 shows the stationary part of the cylinder A - longitudinal cross-section G1-

G1 with an insert made from a material other than that in the Figure 25.

Figure 27 shows the stationary part of the cylinder A - with lining made from a different material.

Figure 28 shows the stationary part of the cylinder A - longitudinal cross-section H-H with an insert made from a material other than that in the Figure 27.

Figure 29 shows the stationary part of the cylinder A - with lining made from a different material, 3D view, isometric.

Figure 30 shows the cover D - front view.

Figure 31 shows the cover D - left side view.

Figure 32 shows the cover D - right side view. Figure 33 shows the cover D - 3D view, isometric.

Figure 34 shows the cover D - with an insert made from a different material or with lining made from a different material.

Figure 35 shows the cover D - cross-section l-l, with an insert or with lining made from a material other than that in the Figure 34.

Figure 36 shows rotor C - front view.

Figure 37 shows rotor C - side view.

Figure 38 shows the rotor C - with an insert made from a different material.

Figure 39 shows rotor C - cross-section J-J with an insert made from a material other than that in the Figure 38.

Figure 40 shows the rotor C - with an insert made from a different material, 3D view, isometric.

Figure 41 shows the rotor C - with lining made from a different material.

Figure 42 shows rotor C - cross-section K-K with lining made from a material other than that in the Figure 41.

Figure 43 shows the rotor C - with lining made from a different material, 3D view, isometric.

Figure 44 shows rotor body with grooves.

Figure 45 shows rotor body with grooves - transversal cross-section L-L in the Figure 44.

Figure 46 shows rotor body with grooves - 3D view, isometric.

Figure 47 shows lateral plates - front view.

Figure 48 shows lateral plates - side view.

Figure 49 shows lateral plates - back view.

Figure 50 shows lateral plates - with an insert made from a different material along the perimeter.

Figure 51 shows lateral plates - the cross-section 0-0 with an insert made from a material other than that in the Figure 50.

Figure 52 shows lateral plates - with an insert made from a different material on the lower surface.

Figure 53 shows lateral plates - the cross-section T-T with an insert made from a material other than that in the Figure 52.

Figure 54 shows lateral plates - with lining made from a different material. Figure 55 shows lateral plates - cross-section Q-Q with lining made from a material other than that in the Figure 54.

Figure 56 shows lateral plates with grooves at the place of sealing.

Figure 57 shows lateral plates - with openings in which move the lateral inserts that lean laterally against the vane.

Figure 58 shows vane with grooves E - perspective view.

Figure 59 shows multi-part vane with grooves E - perspective view.

Figure 60 shows vane machine - with an insert on the cylinder rotating parts made from a different material.

Figure 61 shows vane machine - cross-section M-M with an insert on the cylinder rotating parts made from a material other than that in the Figure 60.

Figure 62 shows vane machine - with lining made from a different material on the cylinder rotating parts.

Figure 63 shows vane machine - cross-section N-N with lining on the cylinder rotating parts made from a material other than that in the Figure 62.

Figure 64 shows vane machine - with an insert on the cylinder stationary parts made from a different material.

Figure 65 shows vane machine - cross-section P-P with an insert on the cylinder stationary parts made from a material other than that in the Figure 64.

Figure 66 shows vane machine - with lining made from a different material on the cylinder stationary parts.

Figure 67 shows vane machine - cross-section R-R with lining on the cylinder stationary parts made from a material other than that in the Figure 66.

Figure 68 shows a vane machine with two cylinder rotating parts between two cylinder stationary parts, with a single additional ring for both rotating parts, with lateral plates in the cylinder stationary parts, and with eccentric openings in covers and rings between lateral plates and bearings and a combination of inlets and lining between cylinder rotating and stationary parts made from a different material.

Figure 69 shows longitudinal cross-section S-S of a vane machine with two cylinder rotating parts between two cylinder stationary parts, with a single additional ring for both rotating parts, with lateral plates in the cylinder stationary parts, with eccentric openings in covers and rings between lateral plates and bearings and a combination of inserts and lining between cylinder stationary and rotating parts made from a material other than that in the Figure 68.

Figure 70 shows isometric view of a vane machine with two cylinder rotating parts between two cylinder stationary parts, with a single additional ring for both rotating parts, with lateral plates in the cylinder stationary parts, with eccentric parts in covers and rings between lateral plates and bearings and a combination of inserts and lining between cylinder stationary and rotating parts made from a different material.

Figure 71 shows a vane machine with three cylinder rotating parts placed on both sides of two cylinder stationary parts, with a single additional ring for both rotating parts, with lateral plates in the cylinder stationary parts, with eccentric openings in covers and rings between lateral plates and bearings and a combination of inserts and lining between cylinder stationary and rotating parts made from a different material. Figure 72 shows longitudinal cross-section X-X of a vane machine with three cylinder rotating parts placed on both sides of two cylinder stationary parts, with a single additional ring for both rotating parts, with lateral plates in the cylinder stationary parts, with eccentric openings In covers and rings between lateral plates and bearings and a combination of inserts and lining between cylinder stationary and rotating parts made from a material other than that in the Figure 71.

Figure 73 shows isometric view of a vane machine with three cylinder rotating parts placed on both sides of two cylinder stationary parts, with a single additional ring for both rotating parts, with lateral plates in the cylinder stationary parts, with eccentric openings in covers and rings between lateral plates and bearings and a combination of inserts and lining between cylinder stationary and rotating parts made from a different material.

Figure 74 shows a vane machine with three cylinder rotating parts between two cylinder stationary parts, with additional rings in the rotating parts and with lateral plates in eccentric openings in covers, and with a combination of inserts and lining between the cylinder rotating and stationary parts made from a different material. Figure 75 shows longitudinal cross-section Y-Y of a vane machine with three cylinder rotating parts between two cylinder stationary parts, with additional rings in the rotating parts and with lateral plates in eccentric openings in covers, and with a combination of inserts and lining between the cylinder stationary and rotating parts made from a material other than that in the Figure 74. Figure 76 shows isometric view of a vane machine with three cylinder rotating parts between two cylinder stationary parts, with additional rings in rotating parts and with lateral plates in eccentric openings in covers, and with a combination of inserts and lining between cylinder stationary and rotating parts made from a different material. Figure 77 shows a vane machine made of several basic vane machines mounted to the same rotor and a combination of inserts and linings between the cylinder stationary and rotating parts made from a different material.

Figure 78 shows longitudinal cross-section Z-Z of a vane machine made of several basic vane machines mounted to the same rotor and a combination of inserts and linings between the cylinder stationary and rotating parts made of a material other than that in the Figure 77.

Figure 79 shows isometric view of a vane machine made of several basic vane machines mounted to the same rotor and a combination of inserts and linings between the cylinder stationary and rotating parts made from a different material.

Figure 80 shows p-v diagram of operating cycle of the driving vane machine with compressible working media.

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

The invention description relates to the vane-machine basic version, the cylinder of which consists of one stationary and two rotating parts.

More complex versions of the vane machine may consist of several stationary and rotating cylinder parts, where all combinations of layouts and sizes, depending on the required technical characteristics, are possible.

The basic vane-machine embodiment, as shown in the Figures 1 , 2 and 3, comprises: cylinder stationary part A, cylinder rotating parts B, rotor C, covers D, and vanes F. On the places of contacts of the cylinder stationary and rotating parts, and on the parts rotating at different velocities, there are inserts or linings made from a material of the hardness lesser by at least HRB 25 than the hardness of the basic material from which the parts in contact are made, which inserts or linings enhance sealing at the places of contact of the cylinder stationary and rotating parts. Cylinder stationary part A

The cylinder stationary part A is shown in the Figures 21 , 22, 23, 24 and 25, viewed from front, side, back, isometric, and in the Figure 26 in the cross-section G1-G1.

The cylinder stationary part A is shaped as a hollow roller, in the centre of its hollow part having the inner shroud 1 with the working surface 2 and the lateral surfaces 3. Within the shroud rotates the rotor C.

At its intake and exhaust, the cylinder stationary part has the openings 4, for the covers D.

In the shroud 1 there is the opening 5, allowing the working media to enter, and the opening 6, allowing the working media to exit the cylinder working chamber. Openings 5 and 6 are rectangular and radial relative to the cylinder. Openings 5 and 6 may be of other shapes as well.

Cylinder rotating parts B

The cylinder rotating parts B may be designed in one of the following two variants:

I - variant with one-part additional ring,

II - variant with two-part additional rings.

Figures 9, 10 and 11 as well as 12, 13 and 14 show the variant I - comprising cylinder rotating parts with a one-part additional ring, that in fact make bearings with the outer ring 7 and the inner ring 8, in which there is firmly inserted the additional ring 10 with the working surface 9. As shown in the Figure 3, the bearings are firmly inserted in the openings 4 of the cylinder stationary part A, leaning against the lateral surface 3 of the shroud 1. The additional rings 10 rotate agitated by the vanes F. The additional rings have inserts or linings or are made from a combination of materials of the hardness lesser by at least HRB 25 than the hardness of the basic material from which the parts in contact are made, which inserts or linings enhance sealing at the places of contact of the cylinder stationary and rotating parts.

Figures 15, 16 and 17 as well as 18, 19 and 20 show the variant II - comprising cylinder rotating parts with a two-part additional ring, that in fact make bearings with the outer ring 7 and the inner ring 8, in which there is firmly inserted the additional ring 10 with the working surface 9. As shown in the Figure 3, the bearings are firmly inserted in the openings 4 of the cylinder stationary part A, leaning against the lateral surface 3 of the shroud 1. The additional rings 10 rotate agitated by the vanes F. The additional rings have inserts or linings or are made from a combination of materials of the hardness lesser by at least HRB 25 than the hardness of the basic material from which the parts in contact are made, which inserts or linings enhance sealing at the places of contact of the cylinder stationary and rotating parts.

The cylinder rotating parts B, in the variants I and II, may be roller or sliding bearings. Figures 15a, 16a and 17a as well as 18a, 19a and 20a show the variant III - comprising cylinder rotating parts with a one-part additional ring. This variant is similar to the variant II, the difference being in the sealing achieved laterally with the cylinder stationary part with the cylinder stationary part A with the insert or the lining being fitted to the cylinder stationary part A.

Rotor C

As shown in the Figures 36 and 37, the rotor C has the shaft 11 , the body 12 with the longitudinal slots 13 and the lateral plates 14. The plates 14 are pulled firmly over the shaft and leaning against the rotor body to close the cylinder working chamber 16 from its lateral sides. In the rotor body there are, under the 90° angle, cut four (the number of slots may differ, 3 or more, which requires also different angles between them) longitudinal slots 13 receiving the vanes F, so that the angle between the vane surface and the rotor radial direction is zero. The rotor rotates in the cylinder working chamber 16, jointly with the plates and the vanes. The rotor rotates in the bearings 15, which may be roller or sliding. The bearings are firmly inserted in the openings 17 of the cover D.

Slots in the rotor body may also be designed to enable the vanes to move under an angle formed by the vane surface and the rotor radial direction.

As shown in the Figures 44, 45 and 46, in the outer surface of the rotor body there may be cut longitudinal grooves 15 that create labyrinth sealing.

The rotor body, Figures 38-43, may have inserts or linings or may be made from a combination of materials of the hardness lesser by at least HRB 25 than the hardness of the basic material from which the parts in contact are made, which inserts or linings enhance sealing at the places of contact of the cylinder stationary and rotating parts. Covers D

As shown in the Figures 30-35, the covers D have openings 17 to receive the bearings 15 in which the rotor rotates. The covers are firmly inserted in the openings 4 of the cylinder stationary part, so that they lean against the outer ring 7 of the cylinder rotating part B. Openings 17 are made eccentric relative to the cover axial axis 19.

Vanes F

The vanes may be made with or without grooves. This invention description relates to a vane machine having rotor with grooved vanes (labyrinth sealing).

The vanes F, Figures 58 and 59, have the body 22 in which, in the central part of the upper surface and between two flat surfaces 23, there are cut axial grooves 24, whereas by the whole length of both lateral narrower surfaces there are cut radial grooves 25. The vanes are inserted in the slots 13 in the rotor body. Length of the vane corresponds to the length of fixed parts of the cylinder 1 and the sum of two lengths of the additional rings 10 (the cylinder rotating parts).

Where the vane consists of three or more parts, more efficient substitution of the vane lateral wear and better sealing are possible.

As the rotor rotates, the vane flat surfaces 23 actuate the inner rings 8 or the inner rings 10, respectively, of the cylinder rotating part.

Functioning of the invention

Views of a closed and assembled vane machine are shown in the Figures 4 - front, 5 - side, 6 - back, 7 - cross-section B1-B1 , and 8 - isometrics.

The vane-machine working chamber 16 is defined by the shroud 1 of the cylinder stationary part A, the additional rings 0 of the cylinder rotating parts B, the plates 14 and the body 12 of the rotor C, as well as the flat surface 23 and the axial grooves 24 of the vanes F. The machine working chamber, at the places of contacts between the cylinder rotating and stationary parts, has inserts or linings or the parts in contact are made from a combination of materials of the hardness lesser by at least HRB 25 than the hardness of the basic material from which the parts in contact are made, which inserts or linings enhance sealing at the places of contact of the cylinder stationary and rotating parts. With regard to the number of the vanes, the working chamber may be divided into two or more parts.

The vane machine works by the principle of creating the tangential force, resulting from the pressure difference at the rotor vanes. The tangential force at the rotor shaft appears as the torque momentum that, besides the working number of revolutions of the machine, generates the engine power. In driving machines (engines), the machine power transforms into the mechanic work available, whereas in working machines (pump) the available power is used to change the working fluid pressure with a given flow.

The vane machine with enhanced sealing among the cylinder stationary and rotating parts is powered by bringing the media through the opening 5 into the cylinder working chamber 16. In this process the working media, due to the pressure difference, makes the rotor to rotate. Media in the space between two vanes leaves the cylinder working chamber 6 through the media exhaust opening at the opposite side of the cylinder, and the cycle repeats.

Rotation of the rotor creates a centrifugal force that pushes the vanes F out of the slots 13, this creating friction between the vane flat surfaces 23 and the cylinder rotating part additional rings 10, which agitate the vanes.

The velocities of sliding of the vanes and the additional rings at the surfaces in contact makes the difference between the momentary peripheral velocities due to the additional ring rotation. In this machine, the said velocity depends on the number of vanes. In case of only one vane in the rotor the relative velocities is zero, whereas in case of several vanes the maximum sliding velocities equals the mean speed resulting from the difference of the vane velocities of the maximum and minimum peripheral velocities relative to the current additional ring rotation velocity.

The vanes are axially movable, leaning against the plates 14 of the rotor C. The plates are firmly connected to the rotor and, therefore, rotate with it. This way it is achieved the minimum relative velocity of sliding between the vane lateral edges and the plates, this again resulting in decrease of the rate of friction wear and increase of mechanical efficiency. The relative velocity between the vane lateral edges and the working- chamber plates results from the vane radial motion. Between the vanes and the cylinder stationary part, or the working surface 2 of the shroud 1 , there is a clearance wherefore there is no mutual contact, which avoids friction wear at this region.

The lateral plates, rotating in eccentric openings of the cylinder stationary parts or in eccentric openings of the covers, at the places of contacts with the vanes, have protrusions, slots or openings that guide lateral inserts with labyrinth-sealing grooves leaning laterally against the vane.

The lateral inserts in the lateral plates, leaning laterally against the vane, have inserts or linings or are made from a combination of materials of the hardness lesser by at least HRB 25 than the hardness of the basic material from which the lateral plates are made, which inserts or linings enhance sealing at the places of contact of the cylinder stationary and rotating parts. Lateral inserts at the places of contacts with the vanes have lateral radial labyrinth-sealing grooves.

The lateral inserts leaning laterally against the vane are moved manually or automatically by means of a spring, by bringing the working medium or by another pressure, that decreases the opening between the vane lateral side and the lateral insert, which decreases the distance between the vane and the lateral insert, resulting in an enhanced sealing at that place.

Pressure of the vanes against the bearing additional ring creates sealing at this region. The pressure may, if necessary, be additionally increased by a spring placed in the vane slot or by providing the vane inner radial surface with the working media of higher pressure, which results in an additional radial force.

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

Enhanced sealing among the cylinder stationary and rotating parts is achieved by fitting, on the parts in contact of the cylinder stationary and rotating parts, of inserts or linings or the parts in contact are made from a material of the hardness lesser by at least HRB 25 than the hardness of the basic material from which the parts in contact are made, where all combinations of distribution of inserts or linings are possible. The above described sealing enhances the volumetric efficiency of the machine. Figure 80 shows p-v diagram of a working cycle of a driving vane machine with stationary and rotating cylinder parts, with enhanced sealing among the cylinder rotating and stationary parts, with a compressible working media.

The work of a vane machine with cylinder stationary and rotating parts, for one rotor revolution, is the algebraic sum of the works of charging, expansion and discharge. The process may be described simply in a closed working cycle with compressible working media. The working chamber charging is isobaric, change of the state from a to b. The expansion process is the change of the working chamber volume from b to c. The working media discharge consists of three stages. The first stage is a sudden expansion from c to c', when the exhaust canals start opening. The second stage of exhaust from c' to d is discharge caused by the working volume decrease. The third stage, from d to a', is compression of the residual working media in the working chamber after closing of the exhaust canals. The last stage of the cycles is charging the working chamber with new working media, wherefore the isochoric pressure suddenly rises from a' to a.

The following equation shows the process and results from the energy equilibrium:

EdQ + dZ_M = dU + dL + dZ_v where:

EdQ is the energy brought in with the working media of the G mass

dU is the inner energy change

dL is the work exchanged with the environment

dZ_M is the energy quantity brought into the working chamber as resulting from losses

dZ_v is the energy quantity not used in the working chamber but taken into the environment with the working media

The last two energy quantities may be determined with the following equations: dZ_M = P_MdG_M and dZ_v= P_vdG_v, where:

P_M is the specific energy of the working media entering the cycles

P_v is the specific energy of the working media leaving the cycles

dG_M is the mass of the new working media entering the working chamber in a single cycle from the environment

dG_v is the mass of the new working media leaving the working chamber in a single cycle into the environment

The primary problem of the vane-machine total efficiency is the volumetric efficiency, resulting from charging and discharging the working media in and from the working chamber (processes a' - a and c - c' - d - a' in the p-v diagram). The volumetric efficiency problem is partly solved by the possibility of maximum utilisation of the stationary part of the working-chamber cylindrical wall for the working-media radial intake and exhaust canals. The structural design enables additional increase of cross- sections of the working-media intake and exhaust canals, since vane does not touch the canals, wherefore the canals may be designed as rectangular openings, which design reaches their largest possible area, which improves conditions of charging and discharging of the vane-machine working chamber. In this machine version remains the problem of air flow between the stationary and the rotating parts of the cylinder, solved by fitting, on the parts in contact of the cylinder stationary and rotating parts, of inserts or linings or the parts in contact are made from a material of the hardness lesser by at least HRB 25 than the hardness of the basic material from which the parts in contact are made, where all combinations of distribution of inserts or linings are possible. This achieves sealing between the cylinder stationary and the rotating parts and enhances the machine total volumetric efficiency.

Another important problem solved by the invention is wearing of sliding surfaces of the stationary and rotating parts that enhances the machine total volumetric efficiency. The vanes may be axially moved, wherefore they lean against the rotor lateral plates. Unlike the existing vane-machine embodiments, where the lateral plates are flat, introducing of lateral plates with protrusions, slots or openings that guide the lateral inserts with the labyrinth-sealing grooves, leaning laterally against the vane, results in enhanced sealing between the vane and the lateral plates and enhances the machine total volumetric efficiency.

Unlike the existing vane-machine embodiments, where the working-chamber lateral plates are static, wherefore the relatively high velocities between the vane lateral edge and the lateral plates cause wear of both surfaces in contact, introduction of lateral rotating plates at the rotor, that close the working chamber, decreases the relative velocities related to the vanes, wherefore the lateral wear caused by friction of vanes and plates is decreased. The relative velocities between the vane lateral edges and the working chamber plates results from the radial motion of the vane only. Decrease of the friction losses improves the machine mechanical efficiency.

Presentation of vane machine with several stationary and rotating cylinder parts

The cylinder stationary and rotating parts may, besides the above described basic vane-machine version, be distributed in several other ways, depending on the required technical characteristics of the machine. Figures 60-79 show several complex embodiments of vane machines with various numbers, forms and mutual positions of cylinder stationary and rotating parts.

In the embodiments presented, the lateral plates 14, rotating together with the rotor C, are placed in eccentric openings in covers D or in the cylinder stationary parts, whereas between the lateral plates 14 and the bearings 15, in which the rotor rotates, there are inserted rings 15'.

In vane machines with several stationary cylinder parts, in each of them are made rectangular openings letting the working fluid in (5) and out (6) of the working chamber 16 of the cylinder, Figures 68-70, or are made with working fluid intakes and exhausts through the vane-machine casing, Figures 77-79. The working-fluid exhaust radial opening may, at the beginning of the exhaust, have the surface cross-section narrowed with a gradual increase of the surface cross-section, aimed to decreasing the noise.

Positioning of the axial grooves 24 on the vanes F is adjusted to the distribution of the rotating parts cylinder parts B, Figures 58 and 59.

On the stationary and rotating cylinder parts in contact there are fitted inserts or linings or the parts in contact are made from a material of the hardness lesser by at least HRB 25 than the hardness of the basic materia! from which the parts in contact are made, that enhances sealing at the places of contacts of the cylinder stationary and rotating parts.

In more complex vane-machine embodiments, the distribution of the cylinder stationary and rotating parts may cause different shapes and distributions of other parts housed in such vane-machine casing.

The above mentioned more complex vane-machine versions do not change the spirit of the invention as presented in the basic version of the vane-machine with stationary and rotating cylinder parts.

7. INVENTION APPLICATION

The vane machine with enhanced sealing among the cylinder stationary and rotating parts may be applied in industry as driving or working machine. When used as a working machine, the imported mechanical work, of a given flow, is transformed into change of pressure of compressible or uncompressible working fluid, and when used as a driving machine, it transforms the primary available pressure of compressible or uncompressible working fluid into mechanical work.

As a working or driving machine with compressible fluid, it is used as: pneumatic tool, in mechanisation of various technological processes, as large Diesel engine starter, compressor, vacuum pump, internal-combustion engine.

As a working or driving machine with uncompressible fluid, it is used with: force, movement and momentum transmission systems in building machines, hydraulic cranes, ship hydraulic systems, machine hydro-drive, and with control, regulation or protection in hydraulic systems aimed to automation of working processes.

As a pump or a hydro-engine, it has two fields of application - with regard to the working fluid. When the working fluid is mineral oil, self-lubrication decreases friction and, therefore, wear of the vanes and the casing, which makes the vane-machine greatest setback. This is applied with force, movement and momentum transmission systems in building machines, hydraulic cranes, ship hydraulic systems, machine hydro-drive, and with control, regulation or protection in hydraulic systems aimed to automation of working processes. Hydraulic vane machines have a wide range of rotation speed. Small inertial forces of its rotating parts often make starting and stopping of the machine easier. When applied with non-lubricant working media, the issue of vane and casing wear remains the main hindrance in vane machines or pumps.

Letters and numbers used in the invention description have the following meanings:

A - stationary part of the cylinder

1 - shroud

2 - shroud working surface

3 - shroud lateral surfaces

4 - lateral openings in the stationary part of the cylinder

5 - working fluid intake

6 - working fluid exhaust

B - rotating parts of the cylinder

7 - outer ring of the cylinder rotating part

8 - inner ring of the cylinder rotating part

9 - inner ring working surface

10 - additional ring

C - rotor

11 - rotor shaft

12 - rotor body

13 - vane slots

14 - rotor lateral plate

14.1 - rotor lateral plates with slots towards the cover D

14.2 - rotor lateral plates with slots towards the vanes F

15 - rotor bearings

16 - cylinder working chamber

D - cover

17 - cover eccentric openings for the rotor bearings 18 - cover openings for the rotor lateral plate 19 - cover axial axis

20 - eccentric-opening axial axis

21 - opening radial axis

F - vanes with grooves

22 - vane body

23 - vane flat parts without grooves

24 - axial grooves

25 - radial grooves

26 - insert

27 - lining

G - vane-machine casing

Claims

PATENT CLAIMS

1. Vane machine with enhanced sealing among the stationary and rotating cylinder parts, belonging to the group of volume rotating machines, that may be used as a driving or a working machine, utilising compressible or non-compressible fluids as the working media, in whose cylinder rotates an eccentrically positioned rotor with vanes, that has one or more stationary cylinder parts (A) and one or more rotating cylinder parts (B); where in more complex vane-machine versions, comprising several stationary and rotating cylinder parts, possible are all combinations of mutual distribution of stationary and rotating parts; where the stationary cylinder part has one or more radial openings letting the working fluid in and one or more radial openings letting the working fluid out of the cylinder working chamber; where the working-media radial outlet begins with a narrowed cross-section that increases gradually; where the cylinder rotating parts are rolling or sliding bearings firmly fitted in the cylinder stationary parts openings or in the casing, freely rotating around the cylinder axis; where the said cylinder rotating parts (B) may be made with the additional ring (10) the width of which may be larger than the bearing width; where the vanes (F) at their upper surface (23) have longitudinal axial grooves (24); where the position of the said longitudinal axial grooves (24) on the vanes (F) is adjusted to the distribution of the cylinder stationary parts (A) and rotating parts (B); where when the rotor rotates, the centrifugal force brings the flat surfaces (23) into contact with the working surface (9) of the inner rings (8) or the additional rings (10), thereby agitating them; where on the vane body (22) lateral sides there are longitudinal radial grooves (25) that make contact with the lateral plates (14) when the rotor rotates; where the lateral plates (14) rotate in the eccentric openings of the cylinder stationary parts (A); where the machine has covers (D) with the eccentric openings (18) in which the lateral plates (14) rotate; where the machine has lateral plates (14) firmly fitted to the rotor (C) with which they rotate at the same angle velocity and around the same axis; wherein the bearing additional ring (10) is made of several mutually connected parts; on the cylinder rotating parts (A), that make contact with the stationary parts (B), it is fitted an insert (26) or a lining (27) made from a material of the hardness lesser by at least HRB 25 than the hardness of the basic material of the parts in contact, that enhances sealing at the places of contact of the cylinder stationary and rotating parts; the bearing additional ring has an insert (26) or a lining (27) made from a material of the hardness lesser by at least HRB 25 than the hardness of the basic material of the bearing additional rings, the cylinder stationary part and the rotating lateral plates, that enhances sealing between the bearing additional rings and the cylinder stationary part on one side and between the bearing additional ring and the rotating lateral plate on the other; the lateral plates (14) rotating in eccentric openings of the cover (D) or in eccentric openings of the cylinder stationary parts (A) have an insert (26) or a lining (27) made from a material of the hardness lesser by at least HRB 25 than the hardness of the lateral plate basic material, that enhances sealing between the lateral plates and eccentric openings of the cover (D) and the cylinder stationary parts (A); the lateral plates, at the places of contact with the vanes, have axial labyrinth-sealing grooves; the rotor (C) has an insert (26) or a lining (27) made from a material of the hardness lesser by at least HRB 25 than the hardness of the rotor basic material, that enhances sealing between the rotor and the cylinder stationary and rotating parts.

2. The vane machine, as claimed in Claim 1 , wherein on the cylinder stationary parts (A) that are in contact with the cylinder rotating parts (B) there are fitted inserts (26) or linings (27) made from a material of the hardness lesser by at least HRB 25 than the hardness of the basic material of the parts in contact, that enhances sealing at the places of contact of the cylinder stationary and rotating parts.

3. The vane machine, as claimed in Claim 1 , wherein on the places of the cylinder stationary and rotating party in contact there are fitted inserts (26) or linings (27) made from a material of the hardness lesser by at least HRB 25 than the hardness of the basic material of the parts in contact, where all combinations of distribution of inserts or lining are possible, that enhances sealing at the places of contact of the cylinder stationary and rotating parts.

4. The vane machine, as claimed in Claim 1 , wherein the places of the cylinder stationary and rotating party in contact are made from one or several materials of hardness lesser by at least HRB 25 than the hardness of the basic material with which they are in contact, that enhances sealing at the places of contact of the cylinder stationary and rotating parts.

5. The vane machine, as claimed in Claim 1 , wherein in its more complex versions, comprising several cylinder stationary and rotating parts, on the places of the cylinder stationary and rotating party in contact there are fitted inserts or linings made from a material of the hardness lesser by at least HRB 25 than the hardness of the basic material of the parts in contact, where all combinations of distribution of inserts or lining are possible, that enhances sealing at the places of contact of the cylinder stationary and rotating parts.

6. The vane machine, as claimed in Claim 1 , wherein the lateral plates (14) at their places of contact with the vanes have protrusions, which protrusions at the places of contact with the vane have longitudinal radial labyrinth-sealing grooves.

7. The vane machine, as claimed in Claim 1 , wherein the lateral plates (14) at their places of contact with the vanes have slots, which slots at the places of contact with the vane have longitudinal radial labyrinth-sealing grooves.

8. The vane machine, as claimed in Claim 1 , wherein the lateral plates (14) at their places of contact with the vanes have openings in which move the lateral inserts, which lateral inserts laterally lean against the vane and at the contacts with the vanes have longitudinal radial labyrinth-sealing grooves.

9. The vane machine, as claimed in Claim , wherein the lateral inserts that laterally lean against the vane have the insert (26) or the lining (27) made from a material of the hardness lesser by at least HRB 25 than the hardness of the basic material of the lateral plates, that enhances sealing between the openings in the lateral plates and the lateral inserts.

10. The vane machine, as claimed in Claim 1 , wherein the lateral inserts (26) leaning laterally against the vane (F) are moved manually or automatically by means of a spring, by bringing the working medium or by another pressure, that decreases the opening between the vane lateral side and the lateral insert.

11. The vane machine, as claimed in Claim 1, wherein the vane consists of three or more parts that enable more efficient substitution of the vane wear.