VANE turbine machine

Abstract

Vane turbine machine with a vane machine (A1,C,E) and a turbine machine (C,R,S) mounted on the same rotor (C) for rotation therewith in the casing (F) and arranged in sequence, such that a flow of working fluid expands in the vane machine (A1,C,E) and subsequently further expands in the turbine stage (C,R,S) to produce mechanical power.

Description

[0001] VANE TURBINE MACHINE

[0002] 1. FIELD OF APPLICATION

[0003] The invention relates to combination of vane and turbine machines from the rotating machine group.

[0004] Combination of vane and turbine machine is an engine for continuously converting working fluid energy into mechanical power, utilizing compressible or incompressible fluids as the working media.

[0005] In the Cooperative Patent Classification, it is classified as Field F - Mechanical engineering; Class F 01 - Machines or engines in general; Subclass F 01 C - Rotary piston or oscillating-pistons machines or engines; Group 13 / 02 - Adaptations of machines or engines for special use, combinations of engines and devices driven thereby, for driving hand-held tools or the like; Subclass F 01 D - Non-positive displacement machines or engines; 15 / 06 Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby; Adaptations for driving, or combinations with, handheld tools or the like, as well as group 1 / 344 of the subclass F01C - Rotary piston or oscillating piston machines having the characteristics covered by two or more groups F01C 1 / 02, F01C 1 / 08, F01C 1 / 22, F01C 1 / 24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members, having the movement defined in group F01C 1 / 08 or F01C 1 / 22 and relative reciprocation between the co-operating members - with vanes reciprocating with respect to the inner member. Also, the invention should be classified in the group 11 / 002 of the subclass F01C - Rotary piston or oscillating piston machines or engines with combination of two or more machines or engines, each bean of rotary-piston or oscillating-piston type of similar working principle.

[0006] Also, the invention should be classified further in following subgroups: B23Q5 / 06, G05B11, B24B47, E21B43 as well as in group B23Q15.

[0007] The invention is primarily used for various pneumatic tools, air motors, spindles, oil and gas production employing vane and turbine machines and is not limited to the application described herein.

[0008] 2. TECHNICAL PROBLEM

[0009] The greatest problem present with volumetric machines, especially with vane volumetric machines is noise, the volumetric losses and the mechanic losses.

[0010] Noise in the vane machine occurs when a vane passes an exhaust canal and the trapped volume of air, with pressure higher than atmospheric pressure, expands into the exhaust canal. Any type of the silencer used to decrease noise level restricts flow, generate back pressure which smoothes the pulsating air flow. Silencer reduces the peak sound energy but also due to generated back pressure reduces output power of the machine and decrease overall machine's effectiveness.

[0011] Vane machine mechanic losses result from friction between the machine's mutually contacting rotating and stationary parts that make parts of the working chamber. The rotating parts of the cylinder have their radial and axial clearances. If axial clearances occur, axial movement of the vane machine rotating parts and friction result with 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.

[0012] Vane machine volumetric losses occur from leaking of the working fluid from a higher into a lower pressure space. The worn parts in contact 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. Vane machine volumetric efficiency depends on efficiency of charging and discharging the working media in and from the working chamber. In the vane machine with stationary and rotating cylinders the working chamber is charged axially in such a way that an additional channel is provided on the casing through which the working fluid is axially distributed to stationary cylinders and vane machine is discharged radially. Mixing between the leakages flows due to clearance between the parts and the main-stream fluid flow in an additional channel leads to the loss of smoothness of main-stream fluid flow and cause loss of volumetric efficiency.

[0013] Consequence of the higher volumetric and mechanical losses is the lower volumetric and mechanical effectiveness of the machine, that is, its low total effectiveness.

[0014] In general, a turbine machine must be operated at high speeds of the turbine rotor stage and high speed of the air flow in order to utilize the air flow most efficiently. The environment where the tool is used, according to the invention, is often full of particles and different fluids which could impair the function of the tool, if they are allowed to enter into critical portions of the tools, for example between moveable components. The turbine machine due to high speed of the air flow need very clean intake fluid as opposed to vane machine which is much less sensitive to fluid conditions due to lower speed of the air flow.

[0015] Turbines aerodynamic losses occur from leaking of the working fluid from a higher into a lower pressure space due to a small gap between the outer radius of the rotating blades and the stationary outer ring. The main source of loss is the mixing between the main-stream flow and the leakage flow. The loss of smoothness of flow is also due to design / curvature of blades, shock waves, heat transfer, cavitations, and viscous effects, which generate secondary flow. Leakage secondary flow interrupt smooth main-stream flow, increases rotor instability and decreases the efficiency of turbine.

[0016] In the turbine there is small gap between the outer radiuses of the rotating blades and the stationary outer ring, so friction exists only in the bearing. If axial clearances occur in rotor bearings, the rotating blades get in contact with the stationary outer ring due to axial movement of the rotating blades and contact results in high resistance or stopping of rotation, friction and increased wear of parts in contact, which significantly decreases the mechanical effectiveness of the machine.

[0017] When producing small size turbines having a small diameter, turbine rotor blades extend from an outer cylindrical surface and there is no problem machining them from the turbine rotor body but it is not practically possible to machine blades in the turbine stator. The radial sizes of the blades in the high pressure stage are as small as a fraction of a millimeter. Such small blades have to be formed integral with the turbine stator by machining or molding. The requirement for smaller blades raises problems in the machining of the turbine stator blades.

[0018] The vane and turbine machine are mounted on the same rotor for rotation therewith in the casing. Vane machine has eccentrically positioned rotor on which there are firmly fitted bearings placed in covers eccentric openings. Turbine stator has also to be disposed within the round casing and eccentrically with the axis of rotor rotation. Function of the speed governor is to limit fluid intake to the machine to a maximum safe speed when unloaded and to maintain a relatively constant speed despite changes in loading. Centrifugal mechanical speed governor is more complex to design and produce than a pneumatic governor. The centrifugal design is more sensitive to speed changes than a pneumatic governor and hence is better suited to machines that experience large fluctuations in loading. A problem concerned with speed control of high speed motors is that mechanical centrifugal speed governors are difficult to get to operate properly at high speed levels due to high dynamic forces, balancing problems, vibrations transmitted to the machine during opening and closing fluid intake. The main problem of centrifugal mechanical speed governor and pneumatic governor is the impossibility of automatically changing the number of revolutions and torque depending on the diameter of the tool used by the machine, the optimal peripheral speed of the measured tool and the torque of the tool. In this way it is not possible to operate machine at the optimal peripheral speed within the working area, to equalize the number of revolutions and torque in case of significant and sudden changes in the working torque of the machine in relation to working surface and automatically reducing the number of revolutions to a minimum or below the revolution range where vibration is present due to resonance between the tool used by the machine and the working surface so the machine works most of the time outside the working area of the tool, the optimal peripheral speed of the tool and the optimal torque of the machine at which the machine's efficiency is greatest. The consequence of the above is the overall low utilization of the machine.

[0019] The technical problem solved by the invention is significantly increasing overall machine's effectiveness and improved energy efficiency with design of the machine in combination of the vane machine and turbine machine, decreasing noise level without decreasing overall machine's effectiveness, turbine stator disposed within the round casing eccentrically with the axis of rotor rotation, decreasing the round casing diameter and weight of tool, low sensitivity to fluid purity, machine oil free work which enables clean working surface and more environmental-friendly operation, increasing efficiency of charging and discharging the working media with divided intake and exhaust canal, increasing smoothness of flow with decreased pressure rises and falls which increases rotor stability, and increases overall machine's effectiveness, decreasing axial movement of the machine rotating parts which increases the mechanical effectiveness of the machine, ensuring smooth operation of the machine by using wave governor spring, automatically changing the optimal peripheral speed of the tool and the optimal torque of the machine at which the machine's efficiency is greatest, reducing vibrations, simpler way to manufacture parts, more cost-effective production and simpler to apply in working conditions.

[0020] 3. STATE OF THE ART

[0021] Vane motors and turbine motors are the most common types of air motors. In the turbine motor the rotation speed is considerably higher than in the vane motor. For both types of motors, speed governors are used to regulate the inflow of air to the motor and thereby limiting to a maximum the rotation speed at idle running.

[0022] Developing and applying history of the vane machine didn't indicate any new solution from state of the art with practical implementation, except vane machine with stationary and rotating parts, publication numbers W02007102033, WO2011021055, WO2014068343 assignee Nebojsa Boskovic. This is caused by insufficient adequate construction or by complex construction which is not adequate for practical in use. This is specially worth for small dimension of the vane machine, which are most frequently uses. In vane machines, the vanes are pressed against the cylinder surfaces in the working chamber by the centrifugal force, in some embodiments additionally by springs or providing the vane inner radial surface with the working-fluid pressure.

[0023] In the first vane machine embodiment, where the cylinder is stationary, the vane machine wear is proportional to the total force pushing the vane against the cylinder surface in the working chamber and to the friction coefficient. The friction problem is solved, among others, by selection of materials of which the vanes and the cylinder are made. In some embodiments the vanes are 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 favorable with regard to the volumetric efficiency.

[0024] In the second vane machine embodiment, where the cylinder has stationary and rotating parts, 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 favorable with regard to the mechanic and volumetric efficiency. Version of second vane machine embodiment with stationary and rotating parts cylinder and decreased wear of the parts in contact, with additionally solved sealing between the rotating and stationary parts enhances the machine's volumetric efficiency. 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 efficiency and life cycle of the machine. Version of second vane machine embodiment with decreased rotating parts clearance also enhances the machine's volumetric efficiency and mechanical efficiency, decreases wear of the parts in contact and extends life cycle of the machine. In second vane machine embodiment, the working chamber is charged axially in such a way that an additional channel is provided on the casing through which the working fluid is axially distributed to all stationary cylinders and axial canal at all stationary cylinders leads to exhaust which is positioned radially relative to the casing. Version of second vane machine embodiment with decreased rotating parts clearance reduces wear of the parts in contact but did not eliminate wear of the parts and axial movement of the parts, because it has part on cylinder designed for wear and after certain time this wearable part is worn. After some time when this wearable part is worn, vane machine has axial movement of parts, axial clearance between stationary and rotating parts of vane machine as well as leakage of fluid and as result reduced machine's volumetric efficiency and mechanical efficiency. Axial movement of vane machine parts shortens considerably the life-cycle of the vane machine, causes vibrations and additional noise. Any axial movement of the machine parts leads to instantaneous contact between the stator and rotor of the turbine, and blocks and destroys the turbine.

[0025] Different versions of silencers are used to reduce noise level in the machine. Any type of the silencer used to decrease noise level restricts flow, generate back pressure which smoothes the pulsating air flow. To reduce noise levels further, a silencer is put into the exhaust pipe where air is exhausted through diffusing holes, which give a controlled pressure drop and reduction in air velocity. To achieve very low noise levels, a two stage silencer are used which cause a large back pressure. To avoid large back pressure in some version active valve with spring is used. It is designed to ensure the pressure in the exhaust pipe is kept almost constant, independent of air flow. As flow rate increases the valve opens, thereby increasing flow area. When flow rate decreases so does the flow area. Any type of silencers from state of the art with practical implementation used to reduce noise level in the machine reduces output power that can be generated by the vane machine and decrease overall machine's effectiveness. Due to the effect of reducing output power, all solutions from state of the art make compromise to reduce noise to acceptable level with as little power reduction as possible.

[0026] Turbines are classified in axial turbines, where the flow of working fluid is substantially parallel to the axis of the rotor, and radial turbines, where the flow of working fluid is substantially radial in at least part of the working fluid path through the turbine.

[0027] An axial turbine is composed of one or more stages in series and each stage consists of one cascade of turbine stator blades that accelerate the flow and one cascade of turbine rotor blades that deflect the flow, converting the enthalpy of the fluid into work as a result of the net change of angular momentum.

[0028] Axial turbines are designed as both action turbines and reaction turbines.

[0029] In action turbines the potential pressure energy in the turbine stator is completely converted into kinetic energy. The flow enters the turbine rotor at atmospheric pressure and under partial admission conditions. Partial admission is used in small- scale turbine stages to enable increased turbine blade height in order to reduce the blade tip leakage loss. Partial admission means that the force of the fluid puts pressure on only some of the blades at any one time.

[0030] In reaction turbines, the turbine rotor inlet pressure is higher than the outlet pressure. The conversion of the potential pressure energy is divided between the turbine stator and turbine rotor. The kinetic energy is then converted into mechanical work at the rotor. The flow enters the turbine rotor at full admission. Full admission means that the working medium flows through the entire circumference of the turbine rotors.

[0031] The turbine machine due to high speed of the air flow need very clean intake fluid as opposed to vane machine which is much less sensitive to fluid conditions due to lower speed of the air flow._The environment where the machine is used is often full of particles and different fluids which could jeopardise the function of the machine if they are allowed to enter into critical portions of the machine, for example between moveable components. All turbines machines from state of the art need very clean intake fluid and are very sensitivity to fluid purity.

[0032] In prior art, it is well known to produce multi-stage turbine machines by forming both the turbine rotor and the turbine stator in a number of sections to be assembled into a complete turbine rotor and a complete turbine stator. In bigger turbines, the blades are formed as separate parts for mounting in rows in the turbine stator, and the turbine stator is divided into two longitudinal halves to be put together around the turbine rotor, whereby the turbine rotor blades rows are introduced between the turbine stator blade rows.

[0033] Small turbines from the state of art have turbine stator in the form of a tubular body which is immovably supported in the housing and which carries internal blades arranged in circumferential rows. The tubular turbine stator body is divided into two or more longitudinal sections with which the blades are integrally formed, like in publication number US6336790, assignee Atlas Copco Industrial Technique. All small turbines from state of the art have centrically disposed turbine stators according to the axis of rotor rotation since it is not possible to obtain eccentrically disposed turbine stators according to the axis of rotor rotation with the existing stator solutions and it is not possible to put vane and turbine machine on the same rotor.

[0034] The rotational speed regulation for small fluid machines are complex and typically one of three types speed governor is used: pneumatic, centrifugal and electronic. There are many different versions of speed governors, like speed control of turbine governed by a pressure air inlet flow controlling valve which is activated by the air pressure in a pressure sensing opening in the turbine stator, speed governor with control of pressurized fluid through one or more reaction nozzles, centrifugal speed governor performed by centrifugal force regulators with elastically deformable wire spring element arranged to be radially bent by centrifugal action to hit and release an airflow restricting element, ball speed governor which includes weights in the form of balls that roll in a conical seat, speed governor comprises an electromagnet actuator and a generator driven by the motor, speed responsive output voltage of a motor driven generator is delivered to the electromagnet actuator.

[0035] 4. ESSENCE OF THE INVENTION

[0036] The essence of the invention is combination of vane and turbine machines for continuously converting of working fluid energy into mechanical power. The invention is used for various pneumatic tools, air motors, spindles, oil and gas production employing vane and turbine machines and is not limited to the tools described herein. A first section of the machine comprises vane machine. A second section of the machine comprises at least one turbine stage. The vane machine and the turbine machine are mounted on the same rotor for rotation therewith in the casing and are arranged in sequence, such that a flow of working fluid expand in the vane machine and subsequently further expand in the turbine stage, to produce mechanical power. The outlet of the vane machine is fluidly coupled to an inlet of the turbine stage through pressure balancing chamber and turbine stage maintain necessary pressure inside vane machine.

[0037] Turbine has a limited working range and generates designed torque and power only in a limited range of the designed number of rpm, while the vane machine generates torque and power in a full range.

[0038] Turbine machine must be operated at high speeds of the turbine rotor and high speed of the air flow in order to utilize the air flow most efficiently while vane machine operates at several times lower speed. The maximum speed of the vane-turbine machine combination is limited by the maximum speed of the vane machine section. Due to a big difference in number of rpm between the turbine and vane machine, the turbine machine in the vane-turbine machine combination works completely outside the working range, so it can generate only a few percent of the designed power.

[0039] Turbine is an energy converter that converts energy of the flowing fluid to the mechanical work. In stator, the potential energy is converted into kinetic energy. Then in rotor, the kinetic energy of the fluid is converted into usable mechanical energy. The energy to be extracted from the fluid is often so large that it is not possible to do in one stage machine design leading to unwanted energy loss.

[0040] Considering that in the vane-turbine machine combination with only one turbine stage, which cannot provide even 10% of the designed power of a multi-stage turbine machine, and considering that the turbine machine in the vane-turbine machine combination works completely outside the working range, so it can generate only a few percent of the designed power it is to be expected that the turbine in such vaneturbine combination does not produce power.

[0041] The outlet of the vane machine is directly fluidly coupled to an inlet of the turbine stage through pressure balancing chamber so it is to be expected that the fluidly coupled turbine restricts flow in the vane machine and generate back pressure which smoothes the pulsating air flow in the vane machine therefore reduces output power that can be generated by the vane machine and decrease overall machine's effectiveness. It is to be expected that in vane-turbine machine combination the vane part has less power and the turbine part does not produce any power, so the whole system has less power.

[0042] Surprisingly it was found that in the vane-turbine machine combination, the turbine stage maintains the required pressure inside the vane machine through a pressure balancing chamber resulting in improved energy efficiency, energy savings and 20% power output increase compared to the most relevant state of the art.

[0043] Moreover, we surprisingly found that the vane-turbine machine combination eliminates speed fluctuations and vibrations transmitted to the machine during opening and closing fluid intake and that the turbine stage maintains the required pressure inside the vane machine through a pressure balancing chamber, resulting in increased smoothness of flow, decreased pressure rises and falls which increases rotor stability and significantly reduces vibrations.

[0044] Noise in the vane machine occurs when a vane passes an exhaust canal and the trapped volume of air, with pressure higher than atmospheric pressure, expands into the exhaust canal. Any type of the silencer used to decrease noise level restricts flow, generate back pressure which smoothes the pulsating air flow. Silencer reduces the peak sound energy but also due to generated back pressure reduces output power of the machine and decrease overall machine's effectiveness. The vaneturbine machine combination with a pressure balancing chamber and the exhaust noise silencing chamber reduces noise without the expected side effect of losing power and reducing overall energy efficiency, but surprisingly with improved energy efficiency, energy savings and increased power compared to the most relevant state of the art.

[0045] Decreasing clearance of rotating parts, by this invention, is solved by non-rotating contact between stationary and rotating cylinders and by clamping nut which is firmly fitted on the rotor that firmly axially fix second stationary cylinder, whole vane machine and the turbine machine eliminating axial movement of parts, axial clearance between stationary and rotating parts of vane machine as well as leakage of fluid. Eliminating axial movement of the vane machine parts containing rotor bearings eliminate also axial clearance between stationary and rotating parts of turbine machine mounted on the same rotor.

[0046] Increasing efficiency of charging and discharging the working media with divided intake and exhaust canal in vane machine increases volumetric efficiency and overall machine's effectiveness.

[0047] Improved machine configuration with decreased clearance due to decreased axial movement of the machine rotating parts, improved turbine configuration with increased efficiency of charging and discharging the working media inside the round casing resulted with decreased casing diameter, increased smoothness of flow, decreased pressure rises and falls which increases rotor stability and increases overall machine's effectiveness. Improved turbine configuration used in the invention not only significantly decreases the aerodynamic losses in turbine but also reduces impact of sensitivity to fluid purity with the turbine blades damages.

[0048] Introduction of a turbine stator made of two part, an inner ring with blades produced in the same way as the turbine rotor blades and an outer ring, firmly fixed to the inner part with blades create simpler way to manufacture parts, more cost-effective production and simpler machine to apply in working conditions. Introduction of a turbine stator outer ring disposed within the round casing eccentrically with the axis of rotor rotation as well as vane machine resulted with decreased casing diameter. Result of the invention is significantly increased overall machine's effectiveness and improved energy efficiency with design of the machine in combination of the vane machine and turbine machine, decreased noise level which occurs when a vane passes an exhaust canal in the vane machine due to last turbine stage, decreased diameter and weight of the tool, machine oil free work which enables clean working surface and more environmental-friendly operation, low sensitivity to fluid purity, smooth operation of the machine by using wave governor spring, simpler way to manufacture parts and more cost-effective production. Automatic regulation of the number of revolutions and torque depending on the parameters that affect the optimal operation of the machine and the work process by electronically controlled air inlet flow controlling valve, which according to predefined parameters regulate the speed of rotation and torque depending on the measured diameter of the tool, measured data on speed of rotation and torque, and the presence of vibrations, enables the gradual achievement of the optimal number of revolutions and torque and the equalization of the number of revolutions in case of significant and sudden changes in the operating torque of the machine and the possibility of memorizing data on request.

[0049] Our patent application contains only partial details of the known state of the art but on the other hand we have made many disclosures in order to present invention. The present invention solves technical problems by introducing combination of different technical features which are simpler to manufacture, more cost-effective and simpler to apply in working conditions. The interactions of all these individual features result in synergistic effect that represent significant progress which significantly increase overall machine's effectiveness, energy saving, improve energy efficiency, reduces noise, decreases vibrations, machine oil free work which enables clean working surface and more environmental-friendly operation, reduces impact of sensitivity to fluid purity, decreases diameter and weight of the tool and increases power compared to the most relevant state of the art.

[0050] 5. BRIEF ILLUSTRATION DESCRIPTION

[0051] Figure 1 shows vane turbine machine - side view.

[0052] Figure 2 shows the vane turbine machine shown in the Figure 1 - perspective view.

[0053] Figure 3 shows the vane turbine machine shown in the Figure 1 - partial longitudinal cross-section A-A.

[0054] Figure 4 shows vane machine - side view.

[0055] Figure 5 shows the vane machine shown in the Figure 4 - perspective view.

[0056] Figure 6 shows the vane machine shown in the Figure 4 - partial longitudinal crosssection B-B.

[0057] Figure 7 shows turbine machine - side view.

[0058] Figure 8 shows the turbine machine shown in the Figure 7 - perspective view.

[0059] Figure 9 shows the turbine machine shown in the Figure 7 - partial longitudinal crosssection C-C.

[0060] Figure 10 shows the first stationary cylinder A1 with axial canal conducting the fluid to the radial working fluid intake into the machine working chamber - side view.

[0061] Figure 11 shows the first stationary cylinder A1 shown in the Figure 10 - perspective view.

[0062] Figure 12 shows the first stationary cylinder A1 - longitudinal cross-section D-D from the Figure 10.

[0063] Figure 13 shows the second stationary cylinder A2 with the radial working fluid exhaust from the machine working chamber and axial canal conducting the fluid - side view.

[0064] Figure 14 shows the second stationary cylinder A2 shown in the Figure 13 - perspective view.

[0065] Figure 15 shows the second stationary cylinder A2 - longitudinal cross-section E-E in the Figure 13.

[0066] Figure 16 shows the rotating cylinder B - side view.

[0067] Figure 17 shows the rotating cylinder B shown in the Figure 16 - perspective view.

[0068] Figure 18 shows the rotating cylinder B - longitudinal cross-section F-F from the Figure 16.

[0069] Figure 19 shows the rotor C with the lateral plates P and turbine connection - side view. Figure 20 shows the rotor C shown in the Figure 19 - side view.

[0070] Figure 21 shows the vane E with longitudinal and transversal grooves and radial slots - perspective view.

[0071] Figure 22 shows casing F for vane turbine machine with working fluid exhausts - side view.

[0072] Figure 23 shows casing F shown in the Figure 22 - front view.

[0073] Figure 24 shows casing F shown in the Figure 22 - perspective view.

[0074] Figure 25 shows the first cover D1 with axial working fluid intake - front view.

[0075] Figure 26 shows the first cover D1 shown in the Figure 25 - perspective view.

[0076] Figure 27 shows the first cover D1 - longitudinal cross-section G-G from the Figure 25.

[0077] Figure 28 shows the second cover D2 with axial working fluid exhaust - front view.

[0078] Figure 29 shows the second cover D2 shown in the Figure 28 - perspective view.

[0079] Figure 30 shows the second cover D2 - longitudinal cross-section H-H from the Figure 28.

[0080] Figure 31 shows the rotor C1 with the lateral plates P and clamping nut - side view.

[0081] Figure 32 shows the rotor C1 shown in the Figure 31 - perspective view.

[0082] Figure 33 shows the rotor C2 with the end plates P1 and parallel key slot - side view.

[0083] Figure 34 shows the rotor C2 shown in the Figure 33 - side view.

[0084] Figure 35 shows the turbine rotor R - side view.

[0085] Figure 36 shows the turbine rotor R shown in the Figure 35 - perspective view.

[0086] Figure 37 shows the turbine rotor RF - side view.

[0087] Figure 38 shows the turbine rotor RF shown in the Figure 37 - perspective view.

[0088] Figure 39 shows the turbine stator inner ring 51 - side view.

[0089] Figure 40 shows the turbine stator inner ring 51 shown in the Figure 39 - side view.

[0090] Figure 41 shows the turbine stator eccentric outer ring 54 - side view.

[0091] Figure 42 shows the turbine stator eccentric outer ring 54 shown in the Figure 41 - side view.

[0092] Figure 43 shows the turbine stator centric outer ring 59 - side view.

[0093] Figure 44 shows the turbine stator centric outer ring 59 shown in the Figure 43 - side view.

[0094] Figure 45 shows the turbine eccentric stator S - side view.

[0095] Figure 46 shows the turbine eccentric stator S shown in the Figure 45 - perspective view.

[0096] Figure 47 shows the turbine centric stator S1 - side view.

[0097] Figure 48 shows the turbine centric stator S1 shown in the Figure 47 - perspective view.

[0098] Figure 49 shows the first cover D3 with axial working fluid intake - front view.

[0099] Figure 50 shows the first cover D3 shown in the Figure 49 - perspective view.

[0100] Figure 51 shows the first cover D3 - longitudinal cross-section l-l from the Figure 49.

[0101] Figure 52 shows the second cover D4 with axial working fluid exhaust - front view. Figure 53 shows the second cover D4 shown in the Figure 52 - perspective view. Figure 54 shows the second cover D4 - longitudinal cross-section J-J from the Figure 52.

[0102] Figure 55 shows machine governor - front view.

[0103] Figure 56 shows the machine governor shown in the Figure 55 - perspective view.

[0104] Figure 57 shows the machine governor shown in the Figure 55 - partial longitudinal cross-section K-K.

[0105] Figure 58 shows load connection - side view.

[0106] Figure 59 shows the load connection shown in the Figure 58 - perspective view.

[0107] Figure 60 shows the load connection shown in the Figure 58 - partial longitudinal cross-section L-L.

[0108] Figure 61 show electronics inside machine - side view. Figure 62 show electronics inside machine shown in the Figure 61 - perspective view.

[0109] Figure 63 show electronics inside machine shown in the Figure 61 - partial longitudinal cross-section.

[0110] Figure 64 shows electronically controlled air inlet flow controlling valve - partial longitudinal cross-section.

[0111] 6. DETAILED DESCRIPTION OF ONE OF THE BEST INVENTION EMBODIMENTS AND ITS FUNCTIONING

[0112] The invention relates to combination of vane and turbine machines. Combination of vane and turbine machines is an engine for continuously converting of working fluid energy into mechanical power utilizing compressible or incompressible fluids as the working media. The invention is primarily used for various pneumatic tools, air motors, spindles, oil and gas production employing vane and turbine machines and is not limited to the application described herein.

[0113] VANE TURBINE MACHINE

[0114] The vane turbine machine with stationary and rotating parts, as shown in the Figures 1 , 2 and 3, consists of the first stationary cylinder A1 , the second stationary cylinder A2, the rotating cylinder B, the rotor C, the governor H, the vanes E, the lateral plates P, the casing F, the covers D1 and D2 in which they are fitted rotor bearings, pressure balancing chamber 45, turbine stator S, turbine rotor R, noise silenced chamber 46 and the fluid exhaust from the machine 44.

[0115] STATIONARY CYLINDERS

[0116] The stationary cylinders are shaped as hollows rollers, in each of them rotating a rotor with vanes.

[0117] The first stationary cylinder - A1

[0118] The first stationary cylinder, A1, Figures 10, 11, 12, consists of: circular raised shroud 1, seal 3, lateral openings 4, circular lateral protruding part 6 and axial working fluid intake canal 2 to radial working fluid intake 5 for the charging fluid to the machine working chamber inside the casing F. The first stationary cylinder A1 has seal 3 in the shroud 1 lateral side facing the covers D1. The first stationary cylinder A1 on the side facing the rotating cylinder B has circular lateral protruding part 6 that touches only the bearing outer ring 9 and there is small gap between the bearing inner ring 10 and the first stationary cylinder A1. The vane machine with axial canal 2 conduct the fluid through the cover D1 and the first stationary cylinder A1 to the working chamber inside the round casing F.

[0119] The second stationary cylinder - A2

[0120] The second stationary cylinder, A2, Figures 13, 14, 15, consists of: circular raised shroud 1, seal 3, lateral openings 4, circular lateral protruding part 6 and axial working fluid exhaust canal 7 from the radial working fluid exhaust 8 for the discharging fluid from the machine working chamber inside the casing F. The second stationary cylinder A2 has seal 3 in the shroud 1 lateral side facing the covers D2. The second stationary cylinder A2 on the side facing the rotating cylinder B has circular lateral protruding part 6 that touches only the bearing outer ring 9 and there is small gap between the bearing inner ring 10 and the second stationary cylinder A2. The radial working fluid exhaust 8 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 vane machine with axial canal 7 conduct the fluid through the cover D2 and the second stationary cylinder A2 from the working chamber inside the round casing F to the fluid exhaust 44 made on the casing F.

[0121] ROTATING CYLINDERS

[0122] Rotating cylinder - B

[0123] The rotating cylinder B, Figures 16, 17 and 18 consists of: two bearings, additional ring 11 with raised shroud 12 and fixed distancer 13. Two bearings are pulled by their inner rings 10 over the flat additional ring with shroud 11. Bearings inner rings 10 are laterally aligned against the shroud 12, on both sides of the shroud 12, thereby decreasing radial and axial clearances of the bearing inner rings 10 and cylinder stationary parts. Between the bearing outer rings 9 is fitted the fixed distancer 13 with identical width as width of raised shoulder 12 to avoid axial movement of bearing outer rings 9. Bearings outer rings 9 are laterally aligned against the circular lateral protruding part 6 of the first stationary cylinder Al and the second stationary cylinder A2, thereby decreasing radial and axial clearances of the bearing outer ring 9 and cylinder stationary parts. There is small gap between the bearing inner ring 10 and the stationary cylinder A1 and A2.

[0124] Figure 3 shows the vane machine with the rotating cylinder 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 14 of the additional ring 11, thus pulling the additional ring 11 with bearings into rotation. More complex versions of rotating cylinders with high precision bearings or sliding bearings 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.

[0125] ROTORS

[0126] As shown in the Figures 19 and 20, rotor C has shaft 15, body 16 with longitudinal slots 17, lateral plates P, clamping nut 56 connections, parallel key slots 19 and connection to load 20. The vane machine lateral plates P are firmly pulled over the shaft 15 and leaned against the rotor body 16, so that they close the vane cylinder chamber with their lateral sides. The rotor C has one or more longitudinal slots 17 for vanes E and one or more longitudinal parallel key slots 19 for fixing turbine rotor R. The rotor C rotates in the cylinder working chamber together with the lateral plates P, the vanes E and turbine rotor R. The rotor C rotates in bearings that are firmly fitted in openings 26 of covers D1 and D2.

[0127] As shown in the Figures 31 and 32, rotor C1 has shaft 15, body 16 with longitudinal slots 17, lateral plates P, clamping nut 56 connection and connection to load 20. The vane machine lateral plates P are firmly pulled over the shaft 15 and leaned against the rotor body 16, so that they close the vane cylinder chamber with their lateral sides. The rotor C1 has one or more longitudinal slots 17 for vanes E. The rotor C1 rotates in the cylinder working chamber together with the lateral plates P and the vanes E. The rotor C1 rotates in bearings that are firmly fitted in openings 26 of covers D1 and D2.

[0128] As shown in the Figures 33 and 34, rotor C2 has shaft 15, body 16 with longitudinal parallel key slots 19, end plate P1, clamping nut 57 connections and connection to load 20. The vane machine end plate P1 are firmly pulled over the shaft 15 and leaned against the rotor body 16, so that they close the turbine working chamber with their lateral sides. The rotor C2 has one or more longitudinal parallel key slots 19 for fixing turbine rotor R. The rotor C2 rotates in the turbine working chamber together with the end plate P1 and turbine rotors R. The rotor C2 rotates in bearings that are firmly fitted in openings 26 of covers D3 and D4.

[0129] Rotor bearings in all embodiments are rolling bearings, high precision paired bearings, sliding bearings, fluid bearings or magnetic bearings. In some embodiments, a combination of different bearings is envisaged as well.

[0130] At one end of the rotor C, C1 and C2 is placed governor H and on one end of the rotor C, C1 and C2 is connection to a load 20, which is driven into rotation by mechanical power generated by the machine.

[0131] In some embodiments the rotor body 16 has one or more axial openings to decrease the rotor mass.

[0132] VANES

[0133] Vanes E are made with or without grooves. The invention example described here is a vane machine that in its rotor C has grooved vanes E, known as the labyrinth seal.

[0134] The vanes E, Figure 21, have body 21 on which are radial slots 22 that take the pressurized working fluid below the vane E into the machine working chamber. In the middle part of the upper surface of the vane E there are flat surfaces 23, whereas at its ends are recessed axial grooves 24, producing labyrinth seal. On both narrower lateral surfaces there are radial grooves 25, producing labyrinth seal by the entire length. The vanes E are inserted into the slots 17 in the rotor body 16. The vane E length equals the sum of lengths of stationary and rotating cylinder parts.

[0135] COVERS

[0136] The vane machine has cover D1 and cover D2, between which are situated stationary and rotating parts of the cylinder. Covers D1 and D2 have openings 26 to receive the bearings 28 in which the rotor C rotates. Openings 26 are made eccentric related to the cover axial axis 29.

[0137] The cover D1 is firmly fitted to the first stationary cylinder A1 , and the cover D2 is firmly fitted to the second stationary cylinder A2, so that they laterally lean against the stationary cylinders shroud 1 with seal 3.

[0138] The turbine machine has cover D3 and cover D4, between which are situated turbine stators S1 and turbine rotors R and RF. Covers D3 and D4 have openings 26 to receive the bearings 28 in which the rotor rotates. Openings 26 are made centric related to the cover axial axis 29.

[0139] Cover D1

[0140] The cover D1, Figures 25, 26 and 27, at its outer surface has axial working fluid intake canal 30. The axial canal 30 leans against the axial canal 2 in the first stationary cylinder A1. Through the axial canals the working fluid flows inside the casing F to the radial opening 5 and, through it, into the vane machine working chamber. The opening 27 in the cover D1 is made eccentric, relative to the axis 29, and in it the lateral plate P firmly fitted to the rotor C rotates.

[0141] Cover D2

[0142] The cover D2, Figures 28, 29 and 30, at its outer surface has axial working fluid exhaust canal 31. The axial canal 31 leans against the axial canal 7 in the second stationary cylinder A2. Working fluid flows out the vane machine working chamber through radial opening 8 to the axial canal 7 in the second stationary cylinder A2 and axial canal 31 in the cover D2 inside the casing F. The opening 27 in the cover D2 is made eccentric,' relative to the axis 29, and in it the lateral plate P firmly fitted to the rotor C rotates. Cover D3

[0143] The cover D3, Figures 49, 50 and 51, at its outer surface has axial working fluid intake canal 30. Through the axial canal 30 the working fluid flows inside the casing F into the turbine machine working chamber. The opening 27 in the cover D3 is made centric, relative to the axis 29, and in it the end plate P1 firmly fitted to the rotor C2 rotates.

[0144] Cover D4

[0145] The cover D4, Figures 52, 53 and 54, at its outer surface has axial working fluid exhaust canal 31. Working fluid flows out the turbine machine working chamber through the axial canal 31 in the cover D4 inside the casing F. The opening 27 in the cover D4 is made eccentric, relative to the axis 29, and in it the rotor C2 rotates.

[0146] TURBINE STATORS

[0147] Turbine stators S

[0148] The turbine stator S, Figures 45 and 46, with blades 53 arranged in circumferential rows is immovably supported by their outer eccentrically ring 54 in the casing F. Turbine stator S is made of two parts, an inner ring 51 with blades 53 produced in the same way as the turbine rotor blades 49 and an outer ring 54, firmly fixed to the inner part with blades.

[0149] Turbine stators S1

[0150] The turbine stator S1, Figures 47 and 48, with blades 53 arranged in circumferential rows is immovably supported by their outer centrically ring 59 in the casing F2. Turbine stator S1 is made of two parts, an inner ring 51 with blades 53 produced in the same way as the turbine rotor blades 49 and an outer ring 59, firmly fixed to the inner part with blades.

[0151] TURBINE ROTORS

[0152] Turbine rotors R

[0153] The turbine rotors R, Figures 35 and 36, with blades 49 arranged in circumferential rows are pulled by their inner ring 47 over the rotor C and fix with parallel key 50 to rotor C and rotate integrally with the rotor C. The turbine rotors R have rotor body distance 58 to the next rotor stage. The turbine rotors blades 49 are disposed in a common way alternating between the rows of stator blades 53.

[0154] Turbine rotors RF

[0155] The turbine rotors RF, Figures 37 and 38, with blades 49 arranged in circumferential rows are pulled by their inner ring 47 over the rotor C2 and fix with parallel key 50 to rotor C2 and rotate integrally with the rotor C2. The last flat rotor RF is firmly fixed to the end plate 55 which is made as integral part of rotor C2 and rotates together with and at the same peripheral velocity as the rotor C2.

[0156] SPEED GOVERNOR

[0157] As shown in the Figures 55, 56 and 57, speed governor H has governor screw 32, governor bushing 33, governor wave spring 43, governor wiper 35, governor chaplet 36, governor pin 38 and at least two governor flyweights 39. The governor wiper 35 is movable along the axial direction of the governor bushing 33 between an open position and a closed position for controlling the fluid pressure flow through the governor cup intake canal 42. The spring is disposed between governor bushing 33 and governor wiper 35 and it is arranged to continuously push the governor wiper 35 in the direction of the open position. Each flyweight is placed in a separate channel 37 of the governor chaplet 36 and fixed with a pin 38 in the opposite walls of the channel. Each flyweight has an extended foot 40 movable by centrifugal action to the governor wiper 35 thereby accomplishing a shifting of the governor wiper 35 in the direction of the closed fluid intake 42 against the force of the spring 43. Speed governor H is fixed to rotor C by the governor screw 32 and rotate integrally with the rotor C.

[0158] MACHINE CASING

[0159] Figures 22, 23 and 24 show the vane turbine machine casing F, in which are fitted the first stationary cylinder A1 , the second stationary cylinder A2, the rotating cylinder B, the rotor C, the vanes E, governor H, the lateral plates P, the covers D1 and D2 in which they are fitted rotor bearings, clamping nut 56, pressure balancing chamber 45, turbine stator S, turbine rotor R, noise silenced chamber 46 and the radial fluid exhaust from the machine 44.

[0160] Vane machine casing F1 is basically identical in configuration to the vane turbine machine casing F shown in the Figure 22, 23 and 24 but different from the vane turbine machine casing F shown in the Figure 22, 23 and 24 in the length required for fitting all vane machine parts. Inside the vane machine casing F1 are fitted the first stationary cylinder A1 , the second stationary cylinder A2, the rotating cylinder B, the rotor C1, the vanes E, governor H, the lateral plates P, the covers D1 and D2 in which they are fitted rotor bearings, clamping nut 56 and the radial fluid exhaust from the machine 44.

[0161] Turbine machine casing F2 is basically identical in configuration to the vane turbine machine casing F shown in the Figure 22, 23 and 24 but different from the vane turbine machine casing F shown in the Figure 22, 23 and 24 in the length required for fitting all turbine machine parts. Inside the turbine machine casing F2 are fitted the turbine stators S, the turbine rotors R and RF, the rotor C2, governor H, the end plate P1, the covers D3 and D4 in which they are fitted rotor bearings, clamping nut 57, noise silenced chamber 46 and the radial fluid exhaust from the machine 44.

[0162] In some casing embodiments fluid exhaust from the machine 44 is placed axially.

[0163] ELECTRONICALLY CONTROLLED AIR FLOW

[0164] Figures 61 , 62 and 63 show electronics inside machine firmly fitted on the rotor and provide data on the number of revolutions, torque, vibrations, electrical energy storage system and transmitters for wireless signal. Some parts of electronics can be placed outside the machine to avoid the influence of fluid impurities. Automated measurement of the tool diameter and detection sensor against damage and breakage of the tool are attached to the front part of the machine. Electronics consist of rotation speed sensor 63, vibration detection sensor 64, torque detection sensor 65, electrical energy storage system 66 inside the machine or connection to an external source of electricity energy, transmitters 67 for wireless signal transmission, sensor 68 for automated measurement of the tool diameter used by the machine, detection sensor 69 against damage and breakage of the tool used by the machine.

[0165] Figure 64 show electronically controlled air inlet flow controlling valve consist of electronic for control air inlet flow controlling valve 61, air inlet flow controlling valve 62, air hose 70 to air inlet flow controlling valve 61 and from air inlet flow controlling valve 61 to the! machine inlet and cable 71 for connecting electronic for control air inlet flow controlling valve 61 with air inlet flow controlling valve 62. FUNCTIONING OF THE INVENTION

[0166] A closed vane turbine machine appearance is shown in the Figure 1, side view, Figure 2, perspective view, and Figure 3, partial longitudinal cross-section A-A of the Figure 1.

[0167] First section of the machine comprises vane machine. Second section of the machine comprises at least one turbine stage. The vane machine and the turbine machine are mounted on the same rotor C for rotation therewith in the casing F and are arranged in sequence, such that a flow of working fluid expand in the vane machine and subsequently further expand in the turbine stage, to produce mechanical power. The outlet of the vane machine is fluidly coupled to an inlet of the turbine stage through pressure balancing chamber 45 and turbine stage maintain necessary pressure inside vane machine. Rotor C is eccentrically positioned in the vane machine on which there are firmly fitted bearings placed in covers eccentric openings. Turbine stator S is disposed within the round casing eccentrically with the axis of rotor C rotation. At one end of the rotor C is placed governor H and on one end of the rotor C is connection to a load 20, which is driven into rotation by mechanical power generated by the machine. Load connection attached to machine is made eccentrically with the axis of rotor C rotation as shown in the Figure 58, 59 and 60.

[0168] The machine operates as follows. A flow of working fluid under pressure enters the vane machine in which part of the working fluid enthalpy is converted into mechanical power available on the rotor C. The partly expanded working fluid enters the turbine stator S where the potential pressure energy delivered from the vane machine is completely converted into kinetic energy that accelerates the flow. The flow enters the turbine rotor R at atmospheric pressure and the turbine rotor blades deflect the flow, converting the enthalpy of the fluid into work as a result of the net change of angular momentum on the rotor C. The exhaust working fluid is then collected in the exhaust noise silencing chamber 46 and discharged from the machine through working fluid exhaust 44.

[0169] The vane machine working chamber is enclosed with inner surfaces of the first stationary cylinder A1 , the second stationary cylinder A2, the rotating cylinder B, the rotor C, the vanes E, the lateral plates P and the covers D1 and D2 in which they are fitted rotor bearings. Depending on the number of vanes E, the working chamber is divided into two or more parts.

[0170] The turbine machine working chamber is enclosed with the turbine rotor R with blades pulled over the rotor C and the turbine stator S with blades which is immovably placed in the casing F.

[0171] Increased efficiency of axially charging and discharging the working media inside the round casing F resulted with decreased casing diameter, increased smoothness of flow, decreased pressure rises and falls which increases rotor stability and increases overall machine's effectiveness.

[0172] The vane machine works by creating tangential force from difference of pressures on the rotor vanes E. The tangential force appears on the rotor shaft 15 as the torque moment that, with the operating number of rotor revolutions, produces power of the machine.

[0173] Vane machine [is put in motion by taking fluid into the working chamber through axial canal 30 of cover D1 , conducting the fluid through the first stationary cylinder axial working fluid intake canal 2 to radial working fluid intake 5 for the charging fluid to the machine working chamber inside the casing F. In working chamber the working fluid due to the pressure difference, makes the rotor C to rotate. The fluid in the space between two vanes E exits the working chamber through radial opening exhaust 8 of the second stationary cylinder A2, and the cycle is repeated. The radial opening 5, conducting fluid into the machine working chamber, is lesser than or equal to the radial opening 8, taking the fluid out. Rotation of the rotor C creates periodical charging and discharging of the working chamber, wherefore, the pressure in the working chamber is decreased from the intake to the exhaust.

[0174] Rotation of the rotor C creates centrifugal power pushing the vanes E out of the slots 17, this creating friction between the flat parts of the vanes 23 and the inner surface 14 of the additional ring 11 of the rotating cylinder B, which pulls the rotating cylinder B into rotation.

[0175] The velocity of sliding between the vanes E and the additional rings 11 at the surfaces in contact is the difference between the current peripheral velocity of the vane E outer edge and the current peripheral velocity resulting from the additional ring 11 rotations. In vane machine, velocity depends on the number of the vanes E. With just one vane E in the rotor C 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 11 rotation speeds.

[0176] In some embodiments the vanes E are moved axially, where they lean against the lateral plates P of the rotor C. The rotating lateral plates P are firmly fitted to the rotor C, laterally closing the working chamber, and rotate together with and at the same peripheral velocity as the rotor C. This results in the minimum relative sliding velocity between the vane E lateral edges and the plates P, this again resulting in lesser wear due to vane E and plates P wearing and, thereby, increased mechanic efficiency. The relative velocity between the vane E lateral edges and the working chamber plates P results only from the vane E radial movement. Between the vanes E and the stationary cylinder A1 and A2 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.

[0177] Edges of the rotor C, at the point of the vane E exiting the slot 17, are angled, to decrease the vane E lateral wear. When vane E with slots is used to remove the pressure building below the vane E, the vanes are pressed against the additional ring of the bearing inner ring 11 only by the centrifugal force, which decreases the vane E pressure power against the bearing additional ring 11 and, thereby, the vane friction and wear.

[0178] In cases of increased axial clearance of rotating parts, the rotating parts make contact with stationary parts, and the rotating parts rotate with a large resistance or stop rotating resulting with wear of parts in contact. This results in a significant increase of mechanical losses within the machine or its complete stoppage. Decreasing of clearance between the 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, enhance the machine volumetric efficiency. Decreasing of clearance of rotating parts, by this invention, is solved by non-rotating contact between stationary and rotating cylinders and by clamping nut 56 which is firmly fitted on the rotor C that firmly axially fix second stationary cylinder A2, whole vane machine and the turbine machine part to avoid axial movement of parts.

[0179] Rotating cylinder B has bearings firmly fitted to the common additional ring with shroud 11 between the bearing inner rings 10 and the fixed distance 13 between the bearing outer rings 9. Lateral side of raised shoulder 12 is made aligned to base of cylinder rotating parts to avoid axial movement of bearing inner rings 10. Between the bearing outer rings 9 there is fixed distancer 13 with identical width as raised shoulder to avoid axial movement of bearing outer rings 9.

[0180] Stationary cylinders A1 and A2 have seal 3 in the cylindrical shroud 1 on the side to the covers D in [order to decrease clearance and leakage of fluid. On the side to the rotating cylinder B, stationary cylinders A1 and A2 on the lateral side in the cylindrical shrotid 1 have a lateral protruding part 6 that touches only the bearing outer ring 9 and there is small gap between the bearing inner ring 10 and the stationary cylinder A1 and A2. The rotating cylinder B is pushed by contact with vanes E into rotation, but only bearing inner ring 10 rotates while the bearing outer ring 9 is stationary, and in firm contact with lateral protruding part 6 of stationary cylinder A1 and A2. In this way non-rotating contact between stationary and rotating cylinders is enabled, eliminating axial movement of parts, axial clearance between stationary and rotating parts of vane machine as well as leakage of fluid.

[0181] Depending on the required degree of precision of decreasing the rotating parts clearance, all mutual combinations of distribution and sizes of elements are possible, 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 machine versions containing rotating parts.

[0182] The issue of the vane machine volumetric efficiency of is partly solved by utilizing as much as possible the space available in the stationary part of the working chamber cylindrical shroud 1 for the working fluid radial intake 5 and radial exhaust 8 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 improves conditions for charging and discharging the vane machine working chamber. Taking the working fluid in and out of the vane machine is improved by placing the stationary cylinders at the end of the cylinders, with the rotating cylinders between them. Between the first stationary cylinders A1 at the machine intake and the casing F there is the axial canal 2 taking the working fluid to the radial opening 5, the machine working chamber intake. The second stationary cylinder A2, at the vane machine exit, has the radial opening 8 to discharge the working fluid from the working chamber to the axial canal 7 taking the working fluid out between the second stationary cylinder A2 and the casing F. The radial working fluid exhaust 8, 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.

[0183] Turbine is an energy converter that converts energy of the flowing fluid to the mechanical work. The fluid contains both potential energy (pressure) and kinetic energy (speed). In a first step, the potential energy is converted into kinetic energy. Then, the kinetic energy of the fluid is converted into usable mechanical energy. The energy to be extracted from the fluid is often so large that it is not possible to do in one stage machine design leading to unwanted energy loss. Design of the machine in combination of vane and turbine machines or turbine machine made of several stages, which are switched in series as a multi-stage turbine machine design, result with machine that extract the most of the energy from the fluid with very high total effectiveness of the machine.

[0184] The turbine rotor R which carries blades 49 arranged in circumferential rows are pulled by their inner ring 47 over the rotor C and fix with parallel key 50 to rotor C and rotate integrally with the rotor C.

[0185] The turbine st tor S which carries blades 53 arranged in circumferential rows is immovably supported by their outer eccentrically ring 54 in the casing F. Turbine stator S is made of two parts, an inner ring 51 with blades 53 produced in the same way as the turbine rotor blades 49 and an outer ring 54, firmly fixed to the inner part with blades. In the turbine tHiere is small gap between the outer radiuses of the rotating blades 53 and the stationary outer ring 54, so friction exists only in the bearing 28. If axial clearances occur in rotor C bearings 28, the rotating blades 53 get in contact with the stationary outer ring 54 due to axial movement of the rotating blades 53 and contact results in high resistance or stopping of rotation, friction and increased wear of parts in contact, which significantly decreases the mechanical effectiveness of the machine.

[0186] Eliminating axial movement of the vane machine parts containing rotor C bearings eliminate also axial clearance between stationary and rotating parts of turbine machine mounted on the same rotor C. Turbine rotor is fixed by clamping nut 56 and connection to load 20 which are firmly fitted on the rotor and turbine stator with firm contact to second stationary cylinders A2 or fixer on casing F.

[0187] Turbine used in this innovation is axial full admission turbine, where the flow of working fluid is substantially parallel to the axis of the rotor C, composed of one or more stages in series and each stage consists of one cascade of turbine stator blades 53 and one cascade of turbine rotor blades 49. Full admission means that the working medium flows through the entire circumference of the turbine rotor. In some embodiments radial and part admission turbine is used.

[0188] The outlet of the vane machine is directly fluidly coupled to an inlet of the turbine stage through pressure balancing chamber 45. The partly expanded working fluid enters the turbine stator S where the potential pressure energy delivered from the vane machine is completely converted into kinetic energy that accelerates the flow and change the flow direction of fluid through stator blades 53 onto the rotor blades 49. The stator blades 53 are arranged to receive the working fluid flow from the rotor blades 49 and divert the flow towards the rotor blades 49. The shape and direction of stator blades 53 direct the flow in the tangential direction of the rotor blades 49. Only tangential velocity increase, the axial velocity does not increase due to conservation of the mass flow rate.

[0189] The flow enters the turbine rotor R at atmospheric pressure and the turbine rotor blades 49 deflect the flow, converting the enthalpy of the fluid into work as a result of the net change of angular momentum on the rotor C. Pressure and enthalpy drop over the rotor blades 49 is minimal, while velocity will decrease while in contact with the rotor blades 49 almost to standstill.

[0190] In the rotor blades 49, the fluid transfers its kinetic energy to the rotor blades 49 by changing its direction. This decreases the tangential velocity, while axial velocity does not change much. The exhaust working fluid is then collected in the exhaust noise silencing chamber 46 and discharged from the machine through working fluid exhaust 44.

[0191] Due to axial flow through turbine blades, the axial turbine has lower aerodynamic losses and higher efficiency.

[0192] The turbine efficiency decreases as the circumferential spacing between blades increases and the total pressure between blades also decreases result with the declining uniformity of fluid flow and the increasing mixing loss of fluid and wake flow between blades which increase fluctuation range of aerodynamic forces to the rotor. The turbine efficiency decreases as the axial gap increases. This is due to declined wake strength and increased the uniformity of wake flow which increased the mixing of the wake and the main flow. Increasing of wake mixing loss between the turbine stator blades exit corners and leading edges of rotors blades gets bigger as the axial gap increases, j

[0193] Turbine machine must be operated at high speeds of the turbine rotor R and high speed of the air flow in order to utilize the air flow most efficiently. The turbine machine, due to high speed of the air flow, needs very clean intake fluid as opposed to vane machine which is much less sensitive to fluid conditions, due to lower flow speed. The environment where the tool is used, according to the invention, is often full of particles and different fluids which could jeopardise the function of the tool if they are allowed to enter into critical portions of the tools, for example between moveable components. Improved turbine configuration used in the invention not only significantly decreases the aerodynamic losses in turbine but also reduces impact of sensitivity to fluid purity with the turbine blades damages. Using light weight materials, necessary in the primary field of use of the machine, which is heat treated and surface protected significantly reduces the impact of air quality on machine operation.

[0194] The governor wiper 35 is movable along the axial direction of the governor bushing 33 between an open position and a closed position for controlling the fluid pressure flow through the governor cup intake canal 42. The spring is disposed between governor bushing 33 and governor wiper 35 and it is arranged to continuously push the governor wiper 35 in the direction of the open position. Each flyweight is placed in a separate channel 37 of the governor chaplet 36 and fixed with a pin 38 in the opposite walls of the channel. Each flyweight has an extended foot 40 movable by centrifugal action to the governor wiper 35 thereby accomplishing a shifting of the governor wiper 35 in the direction of the closed fluid intake 42 against the force of the spring 34.

[0195] When the machine starts to rotate extended foot 40 of each flyweight is movable by centrifugal action to the governor wiper 35 thereby accomplishing a shifting of the governor wiper 35 in the direction of the closed fluid intake 42 against the force of the spring 34.

[0196] The reaction force that the flyweight extended foot 40 presses the governor wiper 35 increases as the rotational speed of the machine increases. When the reaction force of the flyweight extended foot 40 exceed the force of the spring 34, the governor wiper 35 moves to the fluid cup intake 42. When the governor wiper 35 moves to the end of governor bushing 33, the distance between the governor wiper 35 and the fluid cup intake 42 decreases and the supply flow rate decreases. The amount of decrease of the supply flow rate increases as the rotational speed of the machine increases. As a result, the maximum speed of the machine is limited, and the supply flow rate is adjusted so that the rotational speed of the machine does not exceed the allowable speed determined in consideration of safety.

[0197] The speed fluctuations and vibrations transmitted to the machine during opening and closing fluid intake are eliminated by using wave spring 43 in order to ensure smooth operation of the machine.

[0198] In version with pneumatic control valve governor, machine has additional damping chamber controlled in such a way that, through opening and closing pneumatic control valve, rotational speed of the machine is regulated by modulating the pressure and flow of the working medium in the damping chamber to keep rotational speed on same level

[0199] Normally, parts of the vane and turbine 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 and turbine 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.

[0200] In second embodiment only vane machine is used in hard working conditions with very low fluid p'urity and noisy environment, shown in the Figure 4, side view, Figure 5, perspective yiew, and Figure 6, partial longitudinal cross-section of the Figure 4. Vane machine hown in the Figure 4 is basically identical in configuration to the vane motor shown in the Figure 1 but different from the vane machine shown in the Figure 1 in the configuration of the vane machine exhaust through which is fluidly coupled to machine exhaust. Another difference of vane machine shown in the Figure 4 from the vane machine shown in the Figure 1 is that on rotor C1, after clamping nut 56 which firmly axially fix second stationary cylinder A2 and whole vane machine, is connection to a load, which is driven into rotation by mechanical power, generated by the machine.

[0201] In third embodiment only turbine machine is used in working conditions with very high fluid purity and the requirement is to get as much mechanical energy as possible from as small machine as possible, shown in the Figure 7, side view, Figure 8, perspective view, and Figure 9, partial longitudinal cross-section of the Figure 7. Turbine machine shown in the Figure 7 is identical in configuration and characteristics to the turbine machine shown in the Figure 1 but different from the vane turbine machine shown in the Figure 1 in the configuration of the turbine machine. Turbine machine in this embodiment is made of several stages, which are switched in series as a multi-stage turbine machine design, result with machine that extract the most of the energy from the fluid with very high total effectiveness of the machine.

[0202] Rotor C2 is centrically positioned in the turbine machine on which there are firmly fitted bearings 28 placed in covers D3 and D4 openings. At one end of the rotor C2 is placed governor H and on one end of the rotor C2 is connection to a load 20, which is driven into rotation by mechanical power, generated by the machine. Turbine machine in order to utilize the air flow most efficiently, must be operated at high speeds of the turbine rotors and high speed of the air flow, a speed reduction is mostly used instead load connection 20.

[0203] The turbine rotor R which carries blades 49 arranged in circumferential rows are pulled by their inner ring 47 over the rotor C2 and fix with parallel key 50 to rotor C2 and rotate integrally with the rotor C2. The turbine motor shown in FIG. 7 is a six- stage axial type air turbine with 6 stators stage S1 and 5 rotors stage R with rotor body distance 58 to the next rotor stage and last flat rotor stage RF. The turbine rotors blades 49 are disposed in a common way alternating between the rows of stator blades 53. The last flat rotor RF is firmly fixed to the end plate 55 which is made as integral part of rotor C2 and rotates together with and at the same peripheral velocity as the rotor C2.

[0204] The turbine stator S1 which carries blades arranged in circumferential rows is immovably supported by their outer centrically ring in the casing F2. Turbine stator is made of two parts, an inner ring with blades 53 produced in the same way as the turbine rotor blades 49 and an outer ring 59, firmly fixed to the inner part with blades. In this embodiment turbine stators S1 are centrically positioned to the rotor C2. The rotating end plate P1 is firmly fitted to the rotor C2. Between the end plate P1 and the first stator S1 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.

[0205] Bearing 28 which are firmly fitted on the rotor C2 and placed in cover D4 opening on the exhaust side of turbine is axially fixed by clamping nut 57 and end plate 55 which is made as integral part of rotor C2.

[0206] Bearing 28 which are firmly fitted on the rotor C2 and placed in cover D3 opening on the intake side of turbine is axially fixed by end plate P1 and additionally prestressed with bearing preload spring to avoid axial movement of rotating parts.

[0207] Intake of turbin’e machine is directly from machine intake through cover D3 while exhausts working fluid from turbine exits the working chamber through cover D4. A flow of working fluid under pressure enters the first turbine stage and partly expands through first turbine stage. Part of the working fluid enthalpy is converted into mechanical power available on the rotor 02. The partly expanded working fluid enters the neit turbine stage and is further expanded, to generate additional mechanical power available on the rotor C2. The same process of fluid expanding and generating mechanical power available on the rotor C2 continues to last turbine stage. The exhaust working fluid is then collected in the exhaust noise silencing chamber 46 and discharged from the machine through working fluid radial exhaust 44. In some embodiments fluid exhaust from the machine 44 is placed axially.

[0208] In some embodiments of vane turbine machine inside machine there is electronics 61 firmly fitted on the rotor and provide data on the number of revolutions, torque and vibrations. Electronics consist of rotation speed sensor 63, vibration detection sensor 64, torque detection sensor 65, electrical energy storage system 66 inside the machine or connection to an external source of electricity energy, transmitters 67 for wireless signal transmission, sensor 68 for automated measurement of the tool diameter used by the machine, detection sensor 69 against damage and breakage of the tool used by the machine. In some embodiment, electrical power generator is mounted inside the electronic and firmly fitted on the rotor to provide the necessary power to operate the entire electronic circuit. Sensor for rotation speed measures number of revolution and gives a signal to the electronics, which automatically adjust the number of revolutions to the optimal number of revolutions of the machine or below the revolution area. Sensors for detecting torque of the tool measure the torque and give a signal to electronics, which automatically adjust the number of revolutions to the optimal torque range of the machine. Sensor is also used to limit exceeding the value of the torque range for which the machine is pre-programmed. Sensor for detecting vibrations, shocks or blocking of the tool measures the specified parameters and gives a signal to electronics that automatically reduce the number of revolutions to a minimum or below the revolution area where there is resonance between the tool used by the machine and the work surface, and performs automatic balancing in case of poorly balanced tools used by the machine or tool damage. Sensor for automated measurement of the diameter of the tool at the front part of machine performs measurement with or without contact with the tool attached to machine. Some parts of electronics can be placed outside the machine to avoid the influence of fluid impurities. Outside machine is air inlet flow controlling valve controlled by electronics, with the possibility of automatically changing the number of revolutions of the machine and according to predefined parameters regulate the speed of rotation and torque depending on the measured diameter of the tool. In this way it is possible to operate machine at the optimal peripheral speed within the working area, to equalize the number of revolutions and torque in case of significant and sudden changes in the working torque of the machine in relation to working surface, automatically reducing the number of revolutions to a minimum or below the revolution range where vibration is present due to resonance between the tool used by the machine and the working surface, and the possibility of memorizing data on request. Detection sensor against damage and breakage of the tool gives signal to electronic to stop the machine in case of damage or breakage of the tool attached to the machine. Control of electronics for controlling air inlet flow controlling valve for regulation of work, control of correctness of work, indication of malfunction, service and calibration of the machine is possible manually via potentiometer, buttons for regulation, display or some kind of sensor built into the electronics housing or through an external signal source connected to the electronics housing. In this way, it is possible to enter the optimal number of revolutions without the need for automated measurement o)f the diameter of the tool and other data. The aforementioned changes increase the overall utilization of the machine and the efficiency of the process of working with the machine.

[0209] In some embodiments vane turbine machine comprising several stationary and rotating cylinder) parts of vane machine, several turbine stages which are switched in series as a multi-stage vane turbine machine design on the same rotor, aimed to increasing the total power, where all combinations of mutual distribution and sizes of vane stationary cylinder parts, rotating cylinder parts and turbine stages are possible.

[0210] The above mentioned more complex machine embodiments do not alter the spirit of the invention presented in the basic embodiment of the vane turbine machine.

[0211] The tests carried out on eddy current dynamometer produced by Magtrol shows that our innovative vane turbine machines, as result of the invention application described herein, compared with the best existing vane machine on the market with same casing diameter as innovative vane turbine machine, significantly increasing overall machine's effectiveness and improve energy efficiency with design of the machine in combination of the vane machine and turbine machine, decreasing noise level, decreasing the casing diameter and weight of tool. The tests shows that the vane turbine machines prototypes indicated obvious advantages of our construction.

[0212] 7. INVENTION APPLICATION

[0213] Combination of vane and turbine machine is an engine for continuously converting working fluid energy into mechanical power, utilizing compressible or incompressible fluids as the working media.

[0214] The invention is primarily used for various pneumatic tools, air motors, spindles, oil and gas production employing vane and turbine machines and is not limited to the application described herein.

[0215] In some embodiment it is applied in mechanization of various technological processes, as superchargers, fuel cells, starter of large diesel engines, mechanical power source, motion transferring systems, hydraulic cranes, ship hydraulics, hydro powering of processing machines and in hydraulic systems for automation of working processes.

[0216] BRIEF DESCRIPTION OF THE ALPHABETIC AND NUMERIC MARKS USED IN THE INVENTION DESCRIPTION AND ILLUSTRATIONS

[0217] STATIONARY CYLINDERS

[0218] A1 - first stationary cylinder

[0219] A2 - second stationary cylinder

[0220] 1 - shroud

[0221] 2 - axial working fluid intake canal

[0222] 3 - seal in the stationary cylinder lateral side

[0223] 4 - lateral openings of the cylinder stationary parts

[0224] 5 - working fluid radial intake

[0225] 6 - circular lateral shroud

[0226] 7 - axial working fluid exhaust canal

[0227] 8 - working fluid radial exhaust

[0228] ROTATING CYLINDERS

[0229] B - rotating cylinder

[0230] 9 - bearing outer ring

[0231] 10 - bearing inner ring

[0232] 11 - additional ring with shroud

[0233] 12 - shroud on additional ring

[0234] 13 - fixed distancer between the bearing outer rings

[0235] 14 - inner surface of additional ring with shroud ROTOR

[0236] C - rotor with lateral plates P

[0237] 15 - rotor shaft

[0238] 16 - rotor body

[0239] 17 - vane slots

[0240] 18 - clamping nut connection

[0241] 19 - parallel key slots

[0242] 20 - connection to load

[0243] P - lateral plates on rotor

[0244] P1 - end plate on rotor

[0245] C1 - rotor vane

[0246] C2 - rotor turbine

[0247] VANES

[0248] E - vane

[0249] 21 - vane body

[0250] 22 - radial slot taking the working media away

[0251] 23 - flat parts of vanes without grooves

[0252] 24 - axial grooves

[0253] 25 - radial grooves

[0254] COVERS

[0255] D1 - cover with axial intake canal

[0256] D2 - cover with axial exhaust canal

[0257] D3 - cover with axial intake canal

[0258] D4 - cover with axial exhaust canal

[0259] 26 - cover eccentric openings for the rotor bearings

[0260] 27 - cover openings for the rotor lateral plate

[0261] 28 - rotor bearings

[0262] 29 - cover axial axis

[0263] 30 - axial working fluid intake canal

[0264] 31 - axial working fluid exhaust canal

[0265] CASING

[0266] F - vane turbine machine casing

[0267] F1- turbine machine casing

[0268] F2 - vane machine casing

[0269] 44 - fluid exhaust

[0270] 45 - pressure balancing chamber

[0271] 46 - noise silenced chamber

[0272] SPEED GOVERNOR

[0273] H - speed governor

[0274] 32 - speed governor screw

[0275] 33 - speed governor bushing

[0276] 34 - speed governor spring

[0277] 35 - speed governor wiper

[0278] 36 - speed governor chaplet

[0279] 37 - speed governor chaplet channel

[0280] 38 - speed governor pin

[0281] 39 - speed governor flyweights

[0282] 40 - speed governor flyweights extended foot 41 - speed governor cup

[0283] 42 - speed governor cup intake canal

[0284] 43 - speed governor wave spring

[0285] TURBINE

[0286] R - turbine rotor

[0287] R1- turbine rotor flat RF

[0288] S - turbine stator eccentric

[0289] S1 - turbine stator centric

[0290] 47 - turbine rotor inner ring

[0291] 48 - turbine rotor body

[0292] 49 - turbine rotor blades

[0293] 50 - parallel key

[0294] 51 - turbine stator inner ring

[0295] 52 - turbine stator body

[0296] 53 - turbine stator blades

[0297] 54 - turbine stator eccentric outer ring

[0298] 55 - rotor end plate

[0299] 56 - clamping nut vane

[0300] 57 - clamping nut turbine

[0301] 58 - rotor body distance

[0302] 59 - turbine stator centric outer ring

[0303] ELECTRONICALLY CONTROLLED AIR INLET FLOW CONTROLING VALVE

[0304] 60 - electronics inside machine that provide data on the number of revolutions, torque, vibrations and diameter of the tool attached to the machine

[0305] 61 - electronic for control air inlet flow controlling valve

[0306] 62 - air inlet flow controlling valve

[0307] 63 - rotation speed sensor

[0308] 64 - vibration detection sensor

[0309] 65 - torque detection sensor

[0310] 66 - electrical energy storage system

[0311] 67 - transmitters for wireless signal

[0312] 68 - automated measurement of the tool diameter

[0313] 69 - detection sensor against damage and breakage of the tool

[0314] 70 - air hose

[0315] 71 - cable

Claims

CLAIMS1. Vane turbine machine with stationary and rotating cylinder parts, belonging to the rotating machine group, as its working fluid utilizes compressible or incompressible fluids, having two stationary cylinders (A1) and (A2), wherein in the first stationary cylinder (A1) fluid axial intake canal (2) to radial opening (5) is made for charging the fluid into the vane machine working chamber, and stationary cylinders (A1) and (A2) has seal 3 in the shroud 1 on both lateral sides; cylinder rotating parts with two bearings positioned between the stationary cylinders (A1) and (A2), wherein the bearings are by their inner rings (10) pulled over flat additional ring (11) with raised shoulder (12); distancer (13) between the bearing outer rings (9) ; one rotating cylinder (B); eccentrically positioned rotor (C) with lateral plates (P) and vanes (E), wherein at one end of the rotor (C) a governor (H) is placed and on other end of the rotor (C) there is connection to a load (20); casing (F) with additional canal for the working fluid axial distribution; covers (D) closing the machine from its lateral sides, where in the covers (D) there are eccentric openings (26) in which there are firmly fitted the bearings (28) pulled over the rotor (C), wherein in the cover (D1) fluid axial intake canal (30) is made; wire spring regulate speed governor w h e re i n the vane machine and the turbine machine are mounted on the same rotor (C) for rotation therewith in the round casing (F); flow of working fluid partly expand in the vane machine and subsequently further expand in the turbine stage; where turbine stage maintain necessary pressure inside vane machine; the axial canal (31) in cover (D2) leans against the axial canal (7) in the second stationary cylinder (A2), said working fluid flows out the vane machine working chamber through radial opening (8) to the axial canal (7) in the second stationary cylinder (A2) and axial canal (31) in the cover (D2) inside the casing F; the outlet of the vane machine is fluidly coupled to an inlet of the turbine stage through pressure balancing chamber (45); the exhaust working fluid from turbine is collected in the exhaust noise silencing chamber (46) and discharged from the machine through radial working fluid exhaust (44); the rotor (C) has one or more longitudinal slots (17) for vanes (E) and one or more longitudinal parallel key slots (19) for fixing turbine rotor R; the first stationary cylinder (A1) on the side facing the rotating cylinder (B) has circular lateral protruding part (6) that touches only the bearing outer ring (9) and there is small gap between the bearing inner ring (10) and the first stationary cylinder (A1); the second stationary cylinder (A2) on the side facing the rotating cylinder (B) has circular lateral protruding part (6) that touches only the bearing outer ring (9) and there is small gap between the bearing inner ring (10) and the second stationary cylinder (A2); bearings inner rings (10) of the rotating cylinder (B) are laterally aligned against the shroud (12), on both sides of the shroud (12); between the bearing outer rings (9) is fitted the fixed distancer (13) with identical width as width of raised shoulder (12); bearings outer rings (9) are laterally aligned against the circular lateral protruding part (6) of the first stationary cylinder (A1) and the second stationary cylinder (A2); clamping nut (56) which Is firmly fitted on the rotor (C) that firmly axially fix second stationary cylinder (A2) and whole vane machine; the turbine rotor (R) with blades (49) arranged in circumferential rows are pulled by their inner ring (47) over the rotor (C) and fix with parallel key (50) to rotor (C) and rotate integrally with the rotor (C); turbine rotor is fixed by clamping nut (56) and connection to load (20) which are firmly fitted on the rotor; the turbine stator (S) with blades (53) arranged in circumferential rows is immovably supported by their outer eccentrically ring (54)in the casing (F); the turbine stator is made of two parts, an inner ring (51 ) with blades (53) produced in the same way as the turbine rotor blades (49) and an outer ring (54) firmly fixed to the inner ring (51) with blades (53); turbine stator is in firm contact with second stationary cylinders (A2) and casing (F); turbine parts are made from light weight materials which is heat treated and surface protected; wave spring (43) regulate speed governor and ensures smooth operation of the machine without vibrations when opening and closing the fluid supply; wherein the turbine stage maintains the required pressure inside the vane machine through a pressure balancing chamber (45) and the exhaust noise silencing chamber (46) reduces noise without the expected side effect of losing power and reducing overall energy efficiency, but with improved energy efficiency resulting in increased smoothness of flow, decreased pressure variations which increases rotor stability and significantly reduces vibrations, energy savings.

2. Vane turbine machine with stationary and rotating cylinder parts according to the claim 1 wherein the vane machine with stationary and rotating cylinder parts, from the rotating machine group, that is applied as a working machine, that as its working fluid utilizes compressible or incompressible fluids, that has two stationary cylinders; that has one rotating cylinders; that has eccentrically positioned rotor (C) with lateral plates (P) and vanes (E); at one end of the rotor (C) is placed governor (H) and on one end of the rotor (C) is connection to a load (20); that has casing (F) with additional canal for the working fluid axial distribution; that has covers (D) closing the machine from its lateral sides; in the cover (D1) is made fluid axial intake canal (30); in the first stationary cylinder (A1) is made fluid axial intake canal (2) to radial opening (5) charging the fluid into the vane machine working chamber; stationary cylinders (A1) and (A2) has seal 3 in the shroud 1 on both lateral sides; that has cylinder rotating parts with two bearings positioned between the stationary cylinders (A1) and (A2); the bearings are by their inner rings (10) pulled over flat additional ring (11) with raised shoulder (12); between the bearing outer rings (9) there is distancer (13); in the covers (D) there are eccentric openings (26) in which there are firmly fitted the bearings (28) pulled over the rotor (C); wire spring regulate speed governor w h e re i n the vane machine is mounted on the rotor (C) for rotation therewith in the round casing (F); flow of working fluid expand in the vane machine; the axial canal (31) in cover (D2) leans against the axial canal (7) in the second stationary cylinder (A2); working fluid flows out the vane machine working chamber through radial opening (8) to the axial canal (7) in the second stationary cylinder (A2) and axial canal (31) in the cover (D2) inside the casing F; the exhaust working fluid from the vane machine is collected in the exhaust noise silencing chamber (46) and discharged from the machine through radial working fluid exhaust (44); the rotor (C) has one or more longitudinal slots (17) for vanes (E); the first stationary cylinder A1 on the side facing the rotating cylinder (B) has circular lateral protruding part (6) that touches only the bearing outer ring (9) and there is small gap between the bearing inner ring (10) and the first stationary cylinder (A1); the second stationary cylinder (A2) on the side facing the rotating cylinder (B) has circular lateral protruding part (6) that touches only the bearing outer ring (9) and there is small gap between the bearing inner ring (10) and the second stationary cylinder (A2); bearings inner rings (10) of the rotating cylinder (B) are laterally aligned against the shroud (12), on both sides of the shroud (12); between the bearing outer rings (9) is fitted the fixed distancer (13) with identical width as width of raised shoulder (12); bearings outer rings (9) are laterally aligned against the! circular lateral protruding part (6) of the first stationary cylinder (A1)and the second stationary cylinder (A2); clamping nut (56) which is firmly fitted on the rotor (C) firmly axially fix second stationary cylinder (A2) and whole vane machine; wave spring (43) regulate speed governor.

3. Vane turbine machine with stationary and rotating cylinder parts according to the claim 1 wherein the turbine machine, from the rotating machine group, that is applied as a working machine, that as its working fluid utilizes compressible or incompressible fluids, small diameter turbines are axial reaction turbines with partial admission; that has one or more stages in series and each stage consists of one cascade of stator blades and one cascade of rotor blades turbine stator in the form of a tubular body which is immovably supported in the housing; the tubular turbine stator carries internal integrally formed blades arranged in circumferential rows; the tubular turbine stator body is divided into two or more longitudinal sections; at one end of the rotor (C2) is placed governor (H) and on one end of the rotor (C2) is connection to a load (20) wh e re in the turbine machine is a six-stage axial full admission type air turbine with 6 stators stage (S1) and 5 rotors stage (R) with rotor body distance (58) to the next rotor stage and last flat rotor stage (RF); wherein the rotor (C2) is centrically positioned in the machine on which there are firmly fitted bearings (28) placed in covers (D3) and (D4) openings; the rotating end plate (P1) is firmly fitted to the rotor (C2); the turbine rotor (R) and (RF) with blades (49) arranged in circumferential rows are pulled by their inner ring (47) over the rotor (C2) and fix with parallel key (50) to rotor (C2) and rotate integrally with the rotor (C2); the turbine stator (S1) with blades (53) arranged in circumferential rows is immovably supported by their outer centrically ring (59) in the casing (F2); the turbine stator is made of two parts, an inner ring (51) with blades (53) produced in the same way as the turbine rotor blades (49) and an outer ring (59) firmly fixed to the inner ring (51) with blades (53); the turbine rotors blades (49) are disposed in a common way alternating between the rows of stator blades (53). the last flat rotor (RF) is firmly fixed to the end plate (55) which is made as integral part of rotor (C2); bearing (28) which are firmly fitted on the rotor (C2) and placed in cover (D4) opening on the exhaust side of turbine is axially fixed by clamping nut (57) and end plate (55) which is made as integral part of rotor (C2); bearing (28) which are firmly fitted on the rotor (C2) and placed in cover (D3) opening on the intake side of turbine is axially fixed by end plate (P1) and additionally prestressed with bearing preload spring; Intake of turbine machine is directly from machine intake through cover (D3) while exhausts working fluid from turbine exits the working chamber through cover (D4); the exhaust working fluid is then collected in the exhaust noise silencing chamber (46) and discharged from the machine through radial working fluid radial exhaust (44); turbine parts are made from lightweight materials which is heat treated and surface protected; wave spring (43) regulate speed governor.

4. The vane turbine machine, as claimed in Claims 1-3, wh e re in vane-turbine machine has automatic change number of revolutions depending on the optimal peripheral speed of the attached tool and the optimal torque of the machine at which the machine's efficiency is greatest; automatically reducing the number of revolutions tb a minimum or below the revolution range where vibration is present due to resonance between the tool used by the machine and the working surface; inside machine there is electronics (61) provide data on the number of revolutions, torque and vibrations consist of rotation speed sensor (63), vibration detection sensor (64), torque detection sensor (65), electrical energy storagesystem (66) inside the machine or connection to an external source of electricity energy, transmitters (67) for wireless signal transmission; sensor (68) for automated measurement of the tool diameter and detection sensor (69) against damage and breakage of the tool used by the machine attached to the front part of the machine; outside machine are some parts of electronics to avoid the influence of fluid impurities and air inlet flow controlling valve controlled by electronics; electronics operate machine at the optimal peripheral speed within the working area by automatically changing the number of revolutions of the machine and according to predefined parameters regulate the speed of rotation and torque depending on the measured diameter of the tool, equalize the number of revolutions and torque in case of significant and sudden changes in the working torque of the machine in relation to working surface, automatically reducing the number of revolutions to a minimum or below the revolution range where vibration is present due to resonance between the tool used by the machine and the working surface, enables the gradual achievement of the optimal number of revolutions and torque and the equalization of the number of revolutions in case of significant and sudden changes in the operating torque of the machine, stop the machine in case of damage or breakage of the tool attached to the machine and the possibility of memorizing data on request. Control of correctness of work, indication of malfunction, service and calibration of the machine is provided manually via potentiometer, buttons for regulation, display and sensor built into the electronics housing or through an external signal source connected to the electronics housing. In this way it is possible to enter the optimal number of revolutions without the need for automated measurement of the diameter of the tool and other data.

5. Vane machine with stationary and rotating cylinder parts, belonging to the rotating machine group, , as its working fluid utilizes compressible or incompressible fluids, having: two stationary cylinders (A1) and (A2), wherein in the first stationary cylinder (A1) fluid axial intake canal (2) to radial opening (5) is made for charging the fluid into the vane machine working chamber, and stationary cylinders (A1) and (A2) has seal 3 in the shroud 1 on both lateral sides; cylinder rotating parts with two bearings positioned between the stationary cylinders (A1) and (A2), wherein the bearings are by their inner rings (10) pulled over flat additional ring (11) with raised shoulder (12); distancer (13) between the bearing outer rings (9); one rotating cylinder (B); eccentrically positioned rotor (C) with lateral plates (P) and vanes (E), wherein at one end of the rotor (C) governor (H) is placed, and on other end of the rotor (C) there is connection to a load (20); casing (F) with additional canal for the working fluid axial distribution; covers (D) closing the machine from its lateral sides, where in the covers (D) there are eccentric openings (26) in which there are firmly fitted the bearings (28) pulled over the rotor (C), and wherein in the cover (D1) fluid axial intake canal (30) is made;;; ;; ;; wire spring regulate speed governor wh e re in the vane machine with decreasing clearance of rotating parts is enabled by nonrotating contact between stationary (A1) and (A2) and rotating cylinder (B) due to a lateral protruding part (6) that touches only the bearing outer ring (9), said lateral protruding part (6) is placed in the cylindrical shroud (1) on the lateral side of stationary cylinders (A1 ) and (A2) , and due to small gap between the bearing inner ring 10 and the stationary cylinder (A1) and (A2), said vane machine is mounted on the rotor (C) for rotation therewith in the round casing (F); flow of working fluid expand in the vane machine; the axial canal (31) in cover (D2) leans against the axial canal (7) in the second stationary cylinder (A2); workingfluid flows out the vane machine working chamber through radial opening (8) to the axial canal (7) in the second stationary cylinder (A2) and axial canal (31) in the cover (D2) inside the casing F; the exhaust working fluid from the vane machine is collected in the exhaust noise silencing chamber (46) and discharged from the machine through radial working fluid exhaust (44); the rotor (C) has one or more longitudinal slots (17) for vanes (E); the first stationary cylinder A1 on the side facing the rotating cylinder (B) has circular lateral protruding part (6) that touches only the bearing outer ring (9) and there is small gap between the bearing inner ring (10) and the first stationary cylinder (A1); the second stationary cylinder (A2) on the side facing the rotating cylinder (B) has circular lateral protruding part (6) that touches only the bearing outer ring (9) and there is small gap between the bearing inner ring (10) and the second stationary cylinder (A2); bearings inner rings (10) of the rotating cylinder (B) are laterally aligned against the shroud (12), on both sides of the shroud (12); between the bearing outer rings (9) is fitted the fixed distancer (13) with identical width as width of raised shoulder (12); bearings outer rings (9) are laterally aligned against the circular lateral protruding part (6) of the first stationary cylinder (A1) and the second stationary cylinder (A2); wave spring (43) regulate speed governor and ensures smooth operation of the machine without vibrations when opening and closing the fluid supply; divided intake and exhaust canal ensures increasing efficiency of charging and discharging the working media.

6. Vane machine according to any of claims 1, 2 or 5, wherein divided intake and exhaust canal consist of axial working fluid intake canal 2 to radial working fluid intake 5 for the charging fluid to the machine working chamber inside the casing F as intake canal, and axial working fluid exhaust canal 7 from the radial working fluid exhaust 8 for the discharging fluid from the machine working chamber inside the casing F vane machine as exhaust canal.

7. Vane machine according to the any of claims 1, 2 or 5, wherein decreasing clearance of rotating parts is enabled by positioning non-rotating contact between stationary and rotating cylinders and by clamping nut (56) which is firmly fitted on the rotor (C) that firmly axially fix second stationary cylinder (A2), and whole vane machine resulting in elimination of axial movement of parts of the vane machine.

8. The turbine machine, from the rotating machine group, that is applied as a working machine, that as its working fluid utilizes compressible or incompressible fluids, small diameter turbines are axial reaction turbines with partial admission; that has one or more stages in series and each stage consists of one cascade of stator blades and one cascade of rotor blades turbine stator in the form of a tubular body which is immovably supported in the housing; the tubular turbine stator carries internal integrally formed blades arranged in circumferential rows; the tubular turbine stator body is divided into two or more longitudinal sections; at one end of the rotor (C2) is placed governor (H) and on one end of the rotor (C2) is connection to a load (20) wh e re in the turbine machine is a six-stage axial full admission type air turbine with 6 stators stage (S1) and 5 rotors stage (R) with rotor body distance (58) to the next rotor stagd and last flat rotor stage (RF); the rotor (C2) is centrically positioned in the machihe on which there are firmly fitted bearings (28) placed in covers (D3) and (D4) openings; the rotating end plate (P1) is firmly fitted to the rotor (C2); the turbine rotor (R) and (RF) with blades (49) arranged in circumferential rows arepulled by their inner ring (47) over the rotor (C2) and fix with parallel key (50) to rotor (C2) and rotate integrally with the rotor (C2); the turbine stator (S1) with blades (53) arranged in circumferential rows is immovably supported by their outer centrically ring (59) in the casing (F2); the turbine stator is made of two parts, an inner ring (51) with blades (53) produced in the same way as the turbine rotor blades (49) and an outer ring (59) firmly fixed to the inner ring (51) with blades (53); the turbine rotors blades (49) are disposed in a common way alternating between the rows of stator blades (53). the last flat rotor (RF) is firmly fixed to the end plate (55) which is made as integral part of rotor (C2); bearing (28) which are firmly fitted on the rotor (C2) and placed in cover (D4) opening on the exhaust side of turbine is axially fixed by clamping nut (57) and end plate (55) which is made as integral part of rotor (C2); bearing (28) which are firmly fitted on the rotor (C2) and placed in cover (D3) opening on the intake side of turbine is axially fixed by end plate (P1) and additionally prestressed with bearing preload spring; Intake of turbine machine is directly from machine intake through cover (D3) while exhausts working fluid from turbine exits the working chamber through cover (D4); the exhaust working fluid is then collected in the exhaust noise silencing chamber (46) and discharged from the machine through radial working fluid radial exhaust (44); turbine parts are made from light weight materials which is heat treated and surface protected; wave spring (43) regulate speed governor and ensures smooth operation of the machine without vibrations when opening and closing the fluid supply.

9. The vane turbine machine, as claimed in Claims 1-3, wh e re in the exhaust working fluid from the vane turbine machine is discharged from the machine through axial working fluid exhaust.

10. The vane turbine machine, as claimed in Claims 1-3, wh e re in rolling bearings are high precision paired bearings, fluid bearings or magnetic bearings.

11. The vane turbine machine, as claimed in Claims 1-3, wh e re in pneumatic control valve governor has additional damping chamber; rotational speed of the machine is regulated by modulating the pressure and flow of the working medium in the damping chamber to keep rotational speed on same level.

12. The vane turbine machine, as claimed in Claims 1-3, wh e re in parts of the vane and turbine machine are made by casting technology.

13. The vane turbine machine, as claimed in any one of Claims 1-7, comprising several stationary and rotating cylinder parts of vane machine, several turbine stages which are switched in series as a multi-stage vane turbine machine design, all combinations of distribution and sizes of the vane machine parts and the turbine machine parts being possible.

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