Device with centrifugal separator

FIELD: agriculture.

SUBSTANCE: gas purification device contains a centrifugal separator with a centrifugal rotor for separation of particles from gas and the actuating unit for rotation of a centrifugal rotor around a rotation axis. The actuating unit contains the active turbine attached to a centrifugal rotor with a possibility of its driving, and a nozzle for the fluid medium under pressure. The active turbine is implemented with blades for reception of the fluid medium flow under pressure from the nozzle directed towards the blades which are implemented so that the direction of the fluid medium flow is reversed along the blade height. The blade height is 2-3 times greater than the diameter of the nozzle bore.

EFFECT: increase of efficiency of utilisation of energy for driving of a centrifugal rotor at high speeds of rotation at the same flow of the fluid medium under pressure.

14 cl, 4 dwg

 

AREA of TECHNOLOGY

The invention relates to a device for the purification of gas, which is contaminated with particles. The apparatus comprises a centrifugal separator with a centrifugal rotor for separating particles from gas. The device further comprises a driving device for rotation of the centrifugal rotor around the axis of rotation. Driving device contains active turbine, connected to the centrifugal rotor, with the possibility of bringing it into action, and nozzle for a fluid medium under pressure. Impulse turbine is made with blades for making a jet of fluid under pressure from the nozzle is directed towards the blades, which are made so that the direction of the jet of fluid is reversed along the height of the scapula.

Background of the INVENTION

In WO 99/56883 A1 describes a previously known device having a centrifugal separator with a centrifugal rotor for separating particles from the gas. Centrifugal separator is arranged to actuate a fluid medium under pressure, which is generated by an internal combustion engine, wherein the centrifugal rotor is provided with a pneumatic or hydraulic motor, for example, with a turbine, which is arranged to bring into rotation by the fluid under pressure. Driving device of this known device a simple way about�offers very high speed rotation of the centrifugal rotor, and the fact that the centrifugal separator can be positioned at a desired location near the internal combustion engine. This makes the device useful for cleaning of crankcase gas from an internal combustion engine.

In WO 2011/005160 A1 describes another device that includes a centrifugal separator for cleaning crankcase gas from the centrifugal rotor, which provides the fluid under pressure through active turbine. In particular, impulse turbine (shown in more detail in Fig. 1 and 29-34) made with blades for making a jet of fluid under pressure from the nozzle is directed towards the blades. The blades are made so that the direction of the jet of fluid is reversed along the height of the blades. This turbine was both simple and effective to actuate a centrifugal rotor.

These drive devices are often adapted for different operating conditions of the centrifugal separator. One feature is the implementation of a drive unit as efficient as possible. There is a need for conservation of energy consumption to the minimum drive unit, at the same time maintaining and even increasing the separation efficiency of the centrifugal separator.

A BRIEF SUMMARY of the INVENTION

The object of the invention is to increase the efficiency �ipodnova device for a centrifugal separator.

This task is achieved by means specified in the beginning of the device, which is characterized in that the blade height is 2-3 times larger than the diameter of the nozzle aperture.

Formerly known impulse turbine had a height of the blade is roughly five times larger than the diameter of the nozzle aperture. By reducing this height, according to the invention remarkably increases the efficiency of impulse turbine. Thus, the energy for driving the centrifugal rotor is used more efficiently at high speeds. Impulse turbine is optimized for high speed rotation and, therefore, achieves the best separation efficiency of the centrifugal separator. The shorter the distance from which a jet of fluid inside the blade, the better. however, the blade height should not be less than twice the diameter of the jet of fluid, because otherwise it will lead to collision between the incoming part and reversed part of the jet fluid. Such a clash would greatly reduce the efficiency of the turbine.

Blade height is more than three nozzle diameter will also reduce the efficiency of impulse turbine at high rotational speeds. The reason for this is that the rotation of the high speed centrifugal rotor prevents the jet of fluid sufficient �belts to move for a longer distance inside of the scapula and effective reversal. Accordingly, impulse turbine will spin and too much to turn from the nozzle before the jet of fluid will be sufficiently reversed. Therefore, the momentum from the jet of the fluid communicated to the turbine is inefficient. Impulse turbine and a centrifugal rotor can rotate at a speed in the range from 6000 to 14000 rpm. By reducing the height of the turbine according to the invention the jet of fluid is reversed in time and the turbine efficiency is significantly improved in the range of higher speeds. Thus, the new turbine can provide higher output power for driving the centrifugal rotor at speeds of 5000 rpm with the pressure of the fluid and the nozzle size compared to the previously known turbine.

In addition, the invention provides a turbine or driving device of reduced size. This is a very important feature, for example, for cleaning of crankcase gas. When cleaning crankcase gas, the centrifugal separator must be made with possibility of installation in very confined spaces or inside or somewhere around the internal combustion engine of the vehicle. Centrifugal separator drive unit can be installed inside the engine compartment or inside limited�military space inside the internal combustion engine (for example, inside the lid of the cylinder head or valve cover).

In the above-mentioned range 2-3 diameter of the nozzle blade height may be located primarily in the lower region of the range, that is 2 to 2.5 times the diameter of the nozzle bore. Moreover, within this narrowed range, the height may be an average value of 2.3 times larger than the diameter of the nozzle aperture.

Impulse turbine or centrifugal rotor can be either horizontal or vertical axis of rotation. Thus, the term “height” of the blade does not imply a vertical orientation of these components. Vice versa, a impulse turbine and a centrifugal rotor can also be performed with the possibility of rotation around the horizontal axis of rotation. If impulse turbine is regarded as having the form of a cylinder, “height” represents a continuation in the direction of the length of the cylinder.

The jet of fluid may be in the form of gas, but more preferably has the form of a liquid, which generates a higher driving force.

The active radius of the turbine can be advantageously performed so that the ratio between the jet velocity of the fluid and the tangential speed of impulse turbine at the radius where the jet of fluid is made to strike the blades, was 2-3 during operation of the centrifugal separator. So�m, the velocity of the jet of fluid at least 2 times more, but not more than 3 times greater than the tangential velocity of impulse turbine during operation (or, in other words, the tangential velocity of the turbine is 1/3-1/2 the speed of the jet of fluid). Some conditions of operation of the device is set many times. For example, the velocity of the jet of fluid can be set to a specific nozzle or preset working pressure of the fluid. With given input conditions of the turbine will operate at different speeds depending on the applied load. However, the centrifugal rotor is designed to work in a certain load range, which depends on the planned speed of rotation and the amount of gas that flows through the centrifugal rotor in unit time. Accordingly, the radius of the turbine is made in view of these conditions, so that the velocity of the jet fluid was 2-3 times higher than the tangential speed of the turbine. In this range there is the peak power curve of this turbine active.

Thus, the turbine efficiency is additionally increased compared to, for example, with prior active turbine according to WO 2011/005160 A1. Previous turbine had significantly greater radius. In fact, the new radius of the turbine is almost half of the radius of the preceding �Urbina, and, besides, gives a higher speed of rotation at a given pressure of the fluid. Accordingly, the size of the turbine and the driven device is further reduced, and the speed of rotation of the centrifugal rotor is increased. In the above-mentioned range, the active radius of the turbine can be advantageously so designed that the ratio was 2.2 to 2.6. It can also be advantageously designed so that the ratio was 2.4. Accordingly, under the optimal condition of operation of the centrifugal separator, the velocity of the jet of fluid will be 2.4 times greater tangential speed of the turbine at the point where the jet of fluid hits the paddle.

The nozzle bore may be located at a distance of 0.5-5 mm from the impulse turbine. As the jet of fluid exits the nozzle, the diameter of the cone-jet expands, so that it becomes less focused or concentrated as the distance from the nozzle bore. The nozzle bore should be as close to the blade as possible. Thus, the momentum from the jet of the fluid acts on the paddle more efficiently, as a jet of fluid relative to focused close to the nozzle bore. Besides, the closer they are to each other, the greater the diameter of the jet of fluid is similar to the diameter of the hole�I nozzle. Thus, the diameter of the jet of fluid is essentially the same as the diameter of the nozzle aperture when the said distance is short. However, manufacturing tolerances limit the distance up to 0.5 mm, since the shorter the distance there is a risk of damage to the actuator due to collision with each other nozzle and impulse turbine during operation.

The blades of the impulse turbine can be preferably formed with an internal curved part for reversing a fluid medium along the height of the blades, and this inner curved part goes into the outer straight portion extending in a radially outer direction. Direct diverging towards the outside of the blade is made with the possibility of narrowing of the jet of fluid in a curved part of the blade and the expansion of the jet of fluid from it. Thus, if the jet of fluid enters the upper half of the scapula, the upper straight portion directs a jet of fluid in a curved portion, and a lower straight portion directs a jet of fluid from the blade.

As previously mentioned, the centrifugal separator can be advantageously performed with the possibility of cleaning crankcase gas produced by an internal combustion engine during operation, wherein the nozzle is made with the possibility of acceding to the source�the fluid pressure of the internal combustion engine. The device is particularly suitable for cleaning of crankcase gas from a drive unit with a relatively small size. Besides, impulse turbine has been very effective in working bands related to the cleaning of crankcase gas, for example, in relation to the desired high speeds of rotation and is valid centrifugal loads on the rotor. As mentioned previously, the speed of rotation of the centrifugal rotor will typically be in the range 6000-14000 rpm. The centrifugal load on the rotor increases with speed of rotation and the amount of gas which flows through the centrifugal rotor per unit time. The costs of crankcase gas or so-called costs of gas blow-through centrifugal separator can be in the range 40-800 liters per minute depending on the internal combustion engine and its operating conditions. In addition, the fluid preferably is a liquid, and a source of fluid medium under pressure is a liquid pump of the internal combustion engine. The reason for this is that the liquid provides more kinetic energy than gas, because of its higher density.

The source of fluid medium under pressure may be, for example, water or oil pump, which is attached with the possibility of actuation by the internal combustion engine. Suitable�respectively, fluid for actuating impulse turbine can be oil or water, which is compressed by means of the mentioned oil or water pump, respectively. In many cases, the speed of the pump will depend on the speed of the engine, whereby the reduction in motor speed gives a lower pressure fluid from the pump. However, the real impulse turbine is very effective in the above-mentioned ranges and, in particular, when the source of pressure forms a relatively low pressure (e.g., maximum pressure 2-5 bar).

Driving device may be provided with housing for impulse turbine and the nozzle, the housing covers the drive chamber of the centrifugal rotor. This housing may be provided with a wall element, comprising a channel for the nozzle, wherein the channel is connected to the source of fluid medium under pressure into the interface, which is made with possible connection to the internal combustion engine. This provides a simple and effective method for attaching the drive unit to the internal combustion engine. The invention provides the improvement which consists in that may be provided with a very compact body, since the turbine has a reduced size.

BRIEF description of the DRAWINGS

Fig�expiration will be further explained by means of the further description of the embodiment with reference to the accompanying drawings.

Fig.1 shows a longitudinal section of a centrifugal separator having a centrifugal rotor with active turbine.

Fig. 2 shows a kind of impulse turbine and nozzle separately.

Fig. 3 is a view in cross section of impulse turbine and nozzle separately.

Fig. 4 shows a longitudinal section of the blades of the impulse turbine.

DETAILED DESCRIPTION of embodiments of the PRESENT INVENTION

Fig. 1 shows a device for cleaning of crankcase gas from an internal combustion engine. The device includes a centrifugal separator 1 with the centrifugal rotor 2, which is made with possibility of rotation around the axis R of rotation. The centrifugal rotor 2 is located in the separation chamber 3a within a fixed housing 4. Fixed housing 4 has an inlet 5 of the gas, which is made with the possibility of contaminated crankcase gas into the Central space 6 inside the centrifugal rotor 2. The centrifugal rotor 2 includes a package of the separation discs 7a, one above the other. The separation discs 7a are oblong distantsiruyasj elements 7b to provide an axial intermediate spaces 8 for through flow of gas from the Central space 6 and in a radially outer direction. Height distantsiruyutsa elements 7b determines the size of the axial intermediate spaces 8. �only several separation discs 7a are shown with greatly exaggerated dimensions of the intermediate spaces 8. In practice, the centrifugal rotor 2 would include a much greater number of separation discs 7a with much less intermediate spaces 8.

During operation of the centrifugal rotor 2 causes the gas into rotation, whereby the pollutants are separated by centrifugal force as the gas flows through the intermediate space 8 of the centrifugal rotor 2. The intermediate space 8 is open in the radial outer part of the separation chamber 3a which surrounds the centrifugal rotor 2. The purified gas is produced in the outer part of the separating chamber 3a and is discharged from the centrifugal separator 1 through the valve 9a of regulation of pressure and release 9b gas. Valve 9a of the pressure regulation is provided for maintaining the gas pressure inside the crankcase in a safe range. The centrifugal force acting on rotating gas, will make the dirt particles deposited on the surfaces of the separation discs 7a.

The separated contaminants will then be thrown from the separation discs 7a centrifugal rotor 2 against the inner wall of the fixed body 4. The pollutants can then flow down the inner wall to the annular collecting groove 10a which communicates with a drainage issue 10b for removing the collected contaminants from the centrifugal separator 1.

PA�et separation discs 7a is located on the shaft 11, which supports for rotation of the centrifugal rotor 2 in a stationary housing 4. The shaft 11 has a first end 11a, which is supported in a first bearing Assembly 12. The first bearing Assembly 12 has a bearing holder 12a and 12b of the bearing attached to the housing 4 at the inlet 5 of gas. The first holder 12b of the bearing is made in the form of a cap and is located across the inlet 5 of the gas, and the holder 12b of the bearing is provided with holes 12c in order to allow crankcase gases to pass from the inlet 5 of the gas in the Central space 6 inside the centrifugal rotor 2. In addition, the second bearing Assembly 13 is located near the second end 11b of the shaft. Consequently, the first and second bearing assemblies 12, 13 are located at opposite sides of the package separation discs 7a. The second bearing Assembly 13 includes a bearing 13a in the holder 13b of the bearing, which is attached to the housing 4 through the partition 14.

The partition wall 14 divides the interior space of the housing 4 to the separating chamber 3a and the drive chamber 3b. The drive chamber 3b to the centrifugal rotor 2 is shown under the partition 14. The housing 4 has a first housing part 4a for separating chamber 3a and the second housing part 4b to the drive chamber 3b. The first and second housing parts 4a, 4b are connected to each other by means of screws 15, and the burn�dka 14 is located with the possibility of jamming between the hull parts 4a, 4b. The shaft 11 passes through the partition 14 and the drive chamber 3b. The drive chamber 3b covers a driving device for a centrifugal rotor 2. Driving device contains active turbine 16 that is attached to the second end 11b of the shaft with the possibility of bringing it into action. Accordingly, the impulse turbine 16 is made with the possibility of rotation of the centrifugal rotor 2. Impulse turbine 16 is formed with blades 16a for making a jet of oil under pressure from a nozzle (not shown in Fig. 1) directed to the blades 16a. Blade 16a is made so that the direction of the jet of oil was reversibles along the height H of the blade 16a. In this case, the height H of the blade is measured in a vertical direction.

Fig. 2 separately shows the impulse turbine 16 and nozzle 17. Shows the nozzle 17 is located in the wall element 4c of the housing 4b driven camera. The nozzle 17 is connected via a channel (not shown) inside of the wall element 4c to pump the lubricating oil of the internal combustion engine. Thus, when the engine is running, the lubricating oil pump delivers the oil under pressure to the nozzle 17 to the active rotation of the turbine 16 and the centrifugal rotor 2. As shown, the impulse turbine 16 is formed with a Central through hole 16b for connection to the shaft 11. In addition, the upper surface of the impulse turbine 16, directed to the second�Sitnikova node 13, made with a pair of annular ribs 16c. In the installed position of the annular rib 16c surround a portion of the second holder 13b of the bearing for the formation of a labyrinth seal. When the impulse turbine 16 rotates, the separated contaminants from the drainage issue 10b will flow through the second bearing 13a and through the labyrinth seal in the injection pump chamber 3b. The nozzle 17 is located close to the blades 16a with her hole 17a of the nozzle directed to the blades 16a in the tangential direction relative to the turbine 16. It can also be seen in Fig. 3, which shows a cross section of the turbine 16 and the nozzle 17. The momentum from the jet of oil affects the blade 16a is more efficient because the jet of fluid relative to focused close to the holes 17a of the nozzle. In practice, the hole 17a of the nozzle is located at a distance of 0.5-5 mm from the impulse turbine 16.

In addition, the height H of the blades 16a 2-3 times larger than the diameter of the hole 17a of the nozzle. As shown in Fig. 2, the hole 17a of the nozzle is located so as to direct a jet of oil in the upper half of the blade 16a. The inner part of the blade 16a is made with a curvature 16d for reversing the direction of the jet J oil along the height H of the blade 16a (which is also shown in Fig. 4) so that the impulse was communicated to the turbine 16 for rotation of the centrifugal rotor 2. Thus, the jet J oil when�imeetsya in the top half of the blades 16a, in which the stream of oil reverses direction to exit at the lower half of the blade 16a. Impulse turbine with height H was very effective in particular at high speeds of rotation (for example, 6 000-14 000 rpm) of the centrifugal rotor for cleaning of crankcase gas.

Fig. 3 shows a cross section (taken in a horizontal plane) impulse turbine 16 and the nozzle 17 according to Fig. 2. As mentioned above, you can see that the hole 17a of the nozzle toward the blade 16a in the tangential direction of the turbine 16. Jet J oil is ejected at a speed V1 from the hole 17a of the nozzle. The speed V1 of the jet of oil may vary to some extent with the speed of the engine because the oil pump attached to the engine so that the oil pressure will vary with engine speed. Thus, the increase in oil pressure will also increase the speed V1 of the jet of oil, whereby impulse turbine 16 and the centrifugal rotor 2 will rotate faster. The prevailing speed V1 of the jet of oil may be found, for example, by dividing the volumetric flow of oil to the cross sectional area of the hole 17a of the nozzle. Impulse turbine 16 has a tangential velocity V2 of radius R, where a jet of fluid hits the shoulder 16a. As shown in Fig. 3, the radius R represents Soboh� the distance from the center of the impulse turbine 16 to the center of the blade 16a. Impulse turbine 16 with this radius R is of such dimensions that the ratio V1/V2 between the speed V1 of the jet of oil and tangential velocity V2 is 2-3 during operation of the centrifugal separator. Thus, the speed V1 of the jet of oil at least 2 times but not more than 3 times greater tangential speed V2 of impulse turbine of radius R. In this range is the top of the power curve of the turbine, whereby the turbine efficiency is additionally increased compared to previous active turbines for driving the centrifugal rotor.

The speed V1 of the jet of oil can usually be in the range from 20 m/s to 30 m/s during normal operation of the internal combustion engine (for example, heavy truck), and the tangential velocity V2 of radius R is designed to be 1/2-1/3 of the speed V1 of the jet oil. Thus, given the desired high rotational speed (600-14000 rpm) and the actual load on the centrifugal rotor (loss breakthrough of gas 40-800 liters per minute) impulse turbine according to the invention will typically be made with a radius R approximately 10-15 mm. Since the radius R is measured to the center of the blades 16a, radius, measured to the outer circumference of impulse turbine, will be somewhat larger (e.g., longer than 2 or 3 mm). To �e, the diameter of the hole 17a of the nozzle may, for example, be in the range of 2.1-2.9 mm, and the blades 16a have approximately the same width as the diameter of the hole 17a of the nozzle. Consequently, the impulse turbine 16 has a relatively small size.

Fig. 4 shows a cross section along the height H of the blade. Jet J oil shown with large arrows. In addition, the blade 16a is made with a curved part 16d, which is converted into the upper and lower straight portion 16e that radiate outward. Direct radiating outward portion 16e of the blade 16a is made with the possibility of narrowing of the jet J of oil in the bent portion 16d of blade 16a and the expansion of the jet J oil out of it. Thus, as the jet J oil enters the upper half of the scapula, the upper straight portion 16e sends a jet J of oil in the bent portion 16d, and a lower straight portion 16e sends a jet J of the oil from the blade 16a. Direct part 16e of the blade 16a alternatively can be arranged to take place in parallel, in particular if you do not need in direction or narrowing of the jet J of oil in the bent portion 16b of the blade 16a. This may not be necessary, for example, if the hole 17a of the injector well is located within the height H of the blade 16a. The bent portion 16d of the blade 16a is where the direction of the jet J oil is reversed for the message� impulse turbine 16. Therefore, as shown in Fig. 4, the height H of the blades 16a, in fact, measured as the height of only the curved part 16d. However, in practice, the height H can also be measured by the hole of the blade 16a in order, therefore, to include both the bent portion 16b and the straight portion 16e, since this height is almost the same as the height H of the bent portion 16b.

1. Device for the purification of gas, which is contaminated with particles, containing a centrifugal separator (1) with a centrifugal rotor (2) for separating particles from the gas and driving device (16, 17) for rotating the centrifugal rotor (2) around the axis (R) of rotation, wherein the driving device comprises an active turbine (16) connected to the centrifugal rotor (2) with the possibility of bringing it into action, and the nozzle (17) for fluid medium under pressure, and impulse turbine (16) is provided with vanes (16A) for receiving the jet (J) of fluid under pressure from the nozzle (17) is directed towards the blades (16A), which is designed so that the direction of the jet of fluid is reversed along the height (H) of the blade (16A), characterized in that the height (H) of the blade 23 times the diameter of the hole (17A) of the injector.

2. The device according to claim 1, wherein the height (H) of the blade (16A) 22.5 times larger than the diameter of the hole (17A) of the injector.

3. The device p� claim 1, in which the height (H) of the blade (16A) in 2.3 times larger than the diameter of the hole (17A) of the injector.

4. Apparatus according to claim 1, wherein the impulse turbine (16) is made with a radius (R) so that the ratio (V1/V2) between the speed (VI) of the jet fluid and tangential velocity (V2) of the turbine radius (R), where the jet (J) of the fluid strikes the shoulder (16A), is 23 during operation of the centrifugal separator (1).

5. The device according to claim 4, wherein the radius (R) impulse turbine (16) is designed so that the ratio (V1/V2) is 2,22,6.

6. The device according to claim 4, wherein the radius (R) impulse turbine (16) is designed so that the ratio (V1/V2) is 2.4.

7. Device according to any one of claims.1-6, in which the opening (17A) of the nozzle (17) is made at a distance of 0,55 mm from the impulse turbine (16).

8. Device according to any one of claims.1-6, in which the vanes (16A) impulse turbine (16) is provided with inner curved part (16d) for reversing the direction of fluid along the height (H) of the blade (16A), and this inner curved portion (16d) becomes the outer parts direct (16th), diverging in a radially outward direction.

9. Device according to any one of claims.1-6, in which the nozzle (17) is made with possible connection to a source of fluid under pressure motor with internal�of orania, and centrifugal separator (1) is made with the possibility of cleaning crankcase gas produced by an internal combustion engine during operation.

10. The device according to claim 9, in which the fluid is a liquid, and a source of fluid medium under pressure is a liquid pump of the internal combustion engine.

11. The device according to claim 10, wherein the fluid is oil or water, and a source of fluid medium under pressure is oil or water pump, respectively.

12. Device according to any one of claims.1-6, further comprising a housing (4b) for impulse turbine (16) and the nozzle (17), the housing (4b) has a drive chamber (3b) of the centrifugal separator (1).

13. The device according to claim 12, in which centrifugal separator comprises a first frame part (4A) of the centrifugal rotor (2), which is made with possible connection to the second Cabinet portion (4b) forming the housing for active turbine (16) and the nozzle (17).

14. Device according to any one of claims.1-6, in which the centrifugal rotor (2) contains a package of the separation discs (7a) for separating particles from the gas.



 

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EFFECT: higher efficiency of cleaning at minimum hydraulic resistance.

3 cl, 4 dwg

FIELD: oil and gas industry.

SUBSTANCE: device for separating disperse particles from gas contains a body equipped with flanges, with inlet and outlet openings and an opening for liquid removal. Along the perimeter the body is made as multiple-thread helical surface with helical grooves inside the body as curved pockets with centres of the above pockets curvature placed inside cross-section of the body. The body is made of three and more rectangular strips twisted in longitudinal direction along the longitudinal axis and curved along the helix line in longitudinal direction at the cylindrical former thus forming three and more inner curved convex surfaces with the centres of curvature inside the body and forming laps inside the body formed as screw blades along the body length from the inlet opening up to the outlet one. Inside the body there is a helical surface of cylindrical shape with rectangular cross-section of turns; the surface is equipped for turn pitch changing by means of stretching or compression.

EFFECT: improvement of effective separation of disperse particles from gas.

9 dwg

FIELD: oil and gas industry.

SUBSTANCE: gas-liquid separator consists of a body with a fitting pipe for input of gas-liquid mix and fitting pipes for gas and liquid output. Opposite to the fitting pipe for input of gas-liquid mix there is a distributor installed. In the upper part of the separator, there is a web, which central part is made in form of an inverted frustum. In the lower part of the web, there is at least one centrifugal element and at least one drain tube. Underneath of the web there is a case installed covering its central part. The side part of the case is made from funnel-shaped elements repeating the form of the web's central part and installed with a gap in respect of each other. The drain tube is positioned in the case, and the case bottom is equipped with at least one draining pipe with a hydraulic seal installed in the lower part of the separator.

EFFECT: higher efficiency of gas and liquid separation.

1 dwg

Gas cleaner // 2516553

FIELD: process engineering.

SUBSTANCE: invention relates to separator, particularly but not exclusively, to rotary separator for cleaning of liquid-gas. Gas cleaner comprises inner chamber and rotor assembly to swirl the fluid mix. Rotor assembly runs in upper and lower bearings inside said chamber about its axis. Note here that rotor assembly comprises first mix intake pipe, first mix discharge pipe and first flow passage for communication between said first inlet and said first outlet. Outlet is arranged more radially outward the axis than inlet. Separator comprises turbine unit to revolve said rotor assembly. Rotor assembly comprises extra rotary shaft aligned with axis and mounted at the chamber. Rotary shaft first end extends through said chamber to outer position to be coupled with turbine unit. Said rotary shaft has fluid passage extending axially there through. Said passage has bore arranged outside said chamber. Rotary assembly comprises extra flow control means to adjust fluid feed in fluid passage from outside said chamber nearby said turbine unit. Said control means comprises at least one extra fluid passage arranged radially outside the rotary assembly rotational axis to swirl said fluid in line radially outward of said shaft fluid passage.

EFFECT: lubing of upper bearing assembly.

12 cl, 41 dwg

FIELD: devices for trapping of finely dispersed liquid and solid particles from a gas stream.

SUBSTANCE: the invention is intended for trapping of finely dispersed liquid and solid particles from a gas stream in a field of centrifugal forces. The separator contains: a vertical cylindrical body, a horizontal partition, an inlet branch-pipe, an outlet branch-pipe, an overflow connecting pipes, a baffle, a vertical separative package consisting of vertical flat bent separative plates. To raise efficiency of the device and to increase its productivity by liquid and gaseous phases the bent ends of the plates are directed to the different sides in respect to the external and internal diameters of the separative package. The axial line of the inlet branch-pipe is shifted in respect to an axial line of the body of the device by Ѕ of the diameter of the inlet branch-pipe. At that the diameter of the inlet branch-pipe does not exceed 1/4 of the body diameter. The baffle installed on a course of rotation of the gas-liquid stream has the maximum possible cross-section. At that along the course of the stream run it converges in level and increases in height and still keeping the cross-sectional area. At the end of the upper converged part of the baffle there is the arch-shaped plate descending along the run of the gas-liquid stream and directed relatively to a horizontal line at an angle of 15°-30°. Along the course of rotation of the gas-liquid stream with a clearance in respect to the inner side of the body there is a bent plate, which lower ends go under the lower cover of the baffle.

EFFECT: the invention ensures a raise of efficiency and productivity of the device by liquid and gaseous phases.

2 dwg

FIELD: cleaning gases from admixtures, mainly liquid media.

SUBSTANCE: proposed gas drying separator has housing with branch pipes for inlet of non-cleaned gas, escape of cleaned gas and liquid and inlet and outlet filtration sections. Inlet filtration section is made in form of plate mounted above non-cleaned gas inlet branch pipe; this plate is provided with straight-flow centrifugal separation members and gas distributing unit made in form of truncated cone or truncated pyramid widening upward; guide grates with rectangular or square holes are mounted in inlet and intermediate sections. Guide grates are made from vertical flat plates whose height is equal to length of one of sides of square holes or lesser side of rectangular hole; outlet filtration section is made in form of at least two detachable plates located one above other and provided with ring checkerwork; gas distributing grate is located between plates.

EFFECT: enhanced efficiency due to rational delivery of gas and equalizing of velocity field over separator cross-section.

3 cl, 1 dwg

FIELD: purification of gases.

SUBSTANCE: the invention is intended for purification of gases. The separator contains a body with connecting pipes of an inlet and outlet, a linen placed in the body with the fixed on it centrifugal elements including the separation chambers. The body of the separator is made horizontal and the cavity formed by the internal surface of the body, the linen and separation chambers is divided into sections by partitions fixed on the linen and installed between the rows of the centrifugal elements. At that the length of each section exceeds the length of the separating chamber of the centrifugal element. The partitions are made with an inclination to a horizontal plane of the separator. The technical effect: extension of the range of stability of operation and increased efficiency of separation.

EFFECT: the invention ensures extension of the range of stability of operation and increased efficiency of separation.

2 cl, 2 dwg

FIELD: separating dispersed particles from gases or vapors.

SUBSTANCE: dust separator comprises cylindrical housing provided with conical hopper and axial inlet branch pipe arranged in its bottom part, branch pipe for supplying secondary flow and arranged in the top part, and outlet branch pipe. The exit of the inlet branch pipe is provided with the swirler, deflector, and deflecting washer. The swirler is louver and is mounted on the face surface of the cylinder which is the extension of the axial inlet branch pipe or on the conical surface of the deflector which is the extension of the cylinder. The deflecting washer is shaped to define a triangle and is mounted on the side of the cylinder or on the face surface of the cylinder. The diameter of the swirler is greater than that of the inlet branch pipe.

EFFECT: enhanced efficiency of dust separating.

2 cl, 3 dwg

FIELD: separating dispersed particles from gases or vapor.

SUBSTANCE: vortex dust separator comprises housing, axial inlet for dusty gas with swirler and ejecting nozzle, deflector, and deflecting washer, axial branch pipe for discharging purified gas arranged in the top part of the housing, and periphery inlet for secondary flow with swirler. The housing is cylindrical. The deflecting washer is conical, flat or is made of a plate. The ejecting nozzle defines with the inlet wall a ring passage defined by conical or cylindrical surfaces of the axial inlet and ejecting nozzle, respectively. The plane of the exit of the ejecting nozzle is placed above or below the plane of exit of the conical deflecting washer.

EFFECT: enhanced efficiency of separating.

3 cl, 4 dwg

Vortex air cleaner // 2259862

FIELD: physical or chemical processes and apparatus.

SUBSTANCE: vortex air cleaner comprises housing with evacuating chamber provided with one or several separation members each of which consists of separation branch pipes with blade swirlers and outlet branch pipe. The flat blade of the swirlers are interposed between the branch pipes and disks so that the straight outlet edges define inner spaces of the swirlers that have the form of one-space hyperboloids of rotation and are their straight generatrices. The throat periphery of the hyperboloid of the first air swirler is in the space of the disk or in the plane parallel to the disk which is at a distance of the swirler. The throat periphery of the hyperboloid of the second air swirler is in the plane of the disk or plane parallel to the disk and is at a distance of it in the direction opposite to its flowing. The disk of the second air swirler provided with the blades projects out of the separation branch pipe in the direction opposite to the air flow inward to the first separation branch pipe. Before the blade abut against the second separation branch pipe the wall of the second separation branch pipe is provided with rectangular slots for discharging the near-wall air layer with the separated particles to the evacuating chamber.

EFFECT: enhanced efficiency.

10 cl, 4 dwg

FIELD: dust collection processes; chemical, textile, food-processing and light industries.

SUBSTANCE: proposed dust collector has cylindrical chamber with dust receiver located in its lower part and axial inlet for dust-laden gas with baffle washer, peripheral inlet for secondary flow and axial branch pipe for discharge of cleaned gas located in upper part of chamber, rotor made in form of body of revolution and mounted along axis of chamber; this rotor is provided with blade mounted on its surface, direction of winding of this blade coincides with direction of rotation of gas. Free end of rotor located in axial inlet performs function of swirler and fairing for primary flow of dust-laden gas. Axial branch pipe used for discharge of cleaned gas is provided with filter element made in form of washer whose outer surface is secured on inner surface of branch pipe. Rotor blade may be provided on side of axial inlet of dust-laden gas only. Axial branch pipe for discharge of cleaned gas has truncated taper surface whose larger base is secured on branch pipe; rotor passes through center of lesser base at spaced relation.

EFFECT: enhanced efficiency of dust collection due to action of revolving flow on field of velocities.

2 cl, 2 dwg

FIELD: gas producing industry; gaseous throttling separators.

SUBSTANCE: the invention is pertaining to the field of gas producing industry, in particular, to the gaseous throttling separators and may be used in any industry for clearing of gaseous mixtures from a dropping liquid and mechanical impurities and-or for throttling of gases with preservation of the temperature of the inlet gases and with a partial heating. The separator contains a body with bottoms. The body is made out of two coaxially mounted cylindrical shells, the upper of which has a smaller diameter, than the lower. The lower edge of the upper shell is located in the upper part of the lower shell. In the upper part of the separator there are a tangential connecting pipe for a gas feeding and an axial connecting pipe for withdrawal of the gas. The separator is supplied with a liquid phase rejector, the upper edge of which is located so, as to form an annular slot between it and the lower edge of the upper shell. At that the lower part of the liquid phase rejector is made so, as to form an annular chamber for accumulation of the slime, for withdrawal of which the separator has a connecting pipe mounted in the lower shell. Coaxially with the body there is a throttling device made in the form of a pipe connected with the gas withdrawal connection pipe. In the lower part of throttling device made in the form of a pipe there is at least one pair of either coaxially located radial holes or inclined holes located at the similar angle to the axis of the pipe. It is expedient to locate the holes in a chessboard order. Inside the pipe there is a cylindrical adjusting device with a capability of the axial motion for overlapping at least one pair of the indicated holes. Usage of the separator allows to increase a degree of efficiency of the gas cleaning at the expense of organization of the trapped liquid phase with mechanical impurities downward flow, that besides will exclude its secondary entrainment, will ensure heating of gases at the separator outlet and in result the uninterrupted operation of the separator and the following equipment and also a capability to reduce consumption of chemical reactants for prevention of hydrates formation or will allow avoid their usage; will ensure reduction of noise during operation due to the mutual braking of counter meeting streams of the gas coming out of the holes.

EFFECT: the invention ensures improved gas cleaning, uninterrupted operation of the separator, decreased or zero consumption of chemical reactants, prevention of the secondary run of the trapped liquid phase.

8 cl, 1 dwg

FIELD: separation of dispersed particles from gases and vapors by use of gravitational-inertial or centrifugal forces created by turn of gas flow; power engineering; oil producing industry; petrochemical and chemical industries.

SUBSTANCE: proposed separator has housing with flanges and inlet and outlet holes for discharge of liquid. Separator housing is made from guide members in form of three and more strips twisted over helical line in longitudinal direction and bent in transversal direction; they are interconnected by their sides forming helical multi-start hollow column.

EFFECT: enhanced efficiency; reduced hydraulic resistance.

8 dwg

Swirler // 2266155

FIELD: separating dispersed particles from gases.

SUBSTANCE: swirler comprises belt mounted inside the branch pipe and bent over the straight lines at an angle to the edges of the belt to define similar parallelograms arranged on the belt alternatively from the opposite sides. The belt is wound into the cylindrical windings whose longitudinal edges are interconnected to define unidirectional multiple screw lines over the periphery of the outer and inner surfaces and multiple triangle surfaces.

EFFECT: enhanced efficiency and reduced hydraulic resistance.

7 dwg

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