UA138563U - Cyclone and dip tube for separating a gas - Google Patents

Abstract

The invention relates to a dip tube (2) for withdrawing a gas stream from a cyclone (1). During operation the gas flows into the dip tube (2) via a gas inlet (8) and flows out again via a gas outlet (9). The dip tube (2) comprises a first region being designed as a nozzle which convergently tapers from an inner nozzle diameter to a smallest inner diameter, and the dip tube (2) comprises a second region through which during operation downstream the first region gas flows and which is designed as a diffusor which convergently tapers from an inner diffusor diameter in the direction of the first region to the smallest inner diameter. The nozzle has the geometry of a lateral surface being rotationally symmetric with respect to an axis in the form of a truncated cone, wherein the included angle between the lateral surface and the axis is between 15° and 65°.

Description

A useful model is a downpipe for exhausting gas from a cyclone, the gas in operation entering the downpipe through a gas inlet and exiting the downpipe through a gas outlet. For most of the various applications, such as, for example, annular fluidized bed combustion (EBF), flaring, oil recovery, and other processes, it is necessary to remove and/or separate solids from hot waste gases or gas mixtures that contain these solids. particles, before feeding the gas to the next and/or final stage of purification, such as, for example, electrodeposition (EDR), to meet environmental requirements or, in particular, specific product requirements.

As a rule, when applying these processes, gas cyclones are used to filter solid substances in the form of particles from hot waste gas or a mixture of gas products. Such cyclones are also used in steam power plants to separate water from hot steam between the steam generator and the turbine or to separate condensate in gas coolers.

Many important parameters related to the functioning and performance of such a cyclone have already been considered in sufficient quantity. These parameters include pressure, temperature, velocity and gas particle loading, as well as cyclone geometrical parameters. In particular, the cover plate or lid, respectively, of the cyclone, the downpipe, which is also called the "discharge nozzle of the cyclone", and the outlet are important for the discharge of solid particles.

One of the disadvantages of using a cyclone compared to other technologies for the separation of solids and gases is the relatively low efficiency of such separation, in particular in the case of very small particles less than 10 μm in size. The separation efficiency of particles with this size is mainly limited to 90 to 95 95 or even lower.

Since the end of the nineteenth century, many studies have been conducted to determine the effect of individual operating parameters and/or geometric parameters on gas cyclone performance.

This efficiency depends on a series of parameters, such as, for example, particle loading and particle size. Also, the gas velocity inside the cyclone and its individual parts

They have a decisive influence on the performance of the cyclone. The corresponding gas velocities in individual parts of the cyclone are directly influenced by the shape of these parts of the cyclone. In addition, the internal elements of the cyclone, such as, for example, the immersion pipe (cyclone discharge nozzle), the lower part (conical shape of the lower end), the shape of the inlet channel, aeration, etc., directly affect the dust capture and the separation efficiency.

To meet different industrial requirements, there are also different designs of cyclones (vertical or horizontal) depending on the orientation of the inlet (reverse and forward). High-throughput designs are characterized by a shorter body and, in addition, larger openings to provide high-volume throughput. Pressure losses in the case of such a design are often relatively low, and the rate of deposition is also lower. In contrast, designs for higher efficiency are characterized by long bodies and small openings. On the one hand, this design provides high deposition rates, but, on the other hand, leads to high pressure losses.

From patent EP 0 972 572 A? a high-speed countercurrent cyclone containing a cylindrical discharge nozzle is known. This document discloses the relationship between the sizes and shape of individual elements of the cyclone, which ensure particularly high efficiency of the cyclone.

From the document OE 10 2013 207724 A1, a heating installation is known, in which the main combustion takes place in a cyclone-like chamber. The downpipe or discharge nozzle of this cyclonic chamber is shaped like a venturi measuring tray.

An immersion tube or unloading nozzle, which is made of a metal mesh, is known from the patent EP 0 447 802 A2. It consists of several cellular parts.

In general, the efficiency of a well-designed cyclone can be improved by increasing the tangential velocity, but this also results in an increase in pressure loss in the cyclone. However, this increased pressure loss in the cyclone inevitably leads to an increase in pressure loss in the entire system and, thus, to an increase in the demand for electrical energy. In addition, the loss of increased pressure also leads to a higher load on the downpipe, due to the subsequent high pressure gradient between the inner and outer sides of the downpipe.

The task of the useful model is to create a new submersible pipe, which provides the possibility of using a cyclone with high separation efficiency at low pressure losses. This is realized by avoiding high losses at the entrance of underground pipes of small diameters. However, high tangential velocity is achieved by directing to a small diameter inside the nozzle. Since this small cross-section is present only in a relatively short section and the direction to it is realized with a smaller pressure loss, the total pressure loss is reduced, and at the same time the tangential velocity remains almost the same. When adjusting the flow in the same direction and in the next diffuser, part of the lost pressure is additionally restored.

The problem is solved by a submersible pipe for removing gas from a cyclone, in which the gas during operation enters the submersible pipe through the gas inlet and exits through the gas outlet, which is characterized by the fact that the submersible pipe has a first part made as a nozzle narrowing from the inner diameter (Oile) of the nozzle to the smallest inner diameter (a), and a second part through which the gas flows during operation after the first part, and which is designed as a diffuser, narrowing from the inner diameter of the diffuser in the direction of the first part to the smallest internal diameter (a), and the fact that the nozzle has the shape of a side surface, rotationally symmetrical with the axis, in the form of a truncated cone, and the angle (o) of the cone between the side surface and the axis is 157-657.

The downpipe, according to a useful model, containing the inner diameter (O;ppeu) of the nozzle is 1.2-8 of the smallest inner diameter (4), the length (H) of the nozzle from the inner diameter (Oipte) of the nozzle to the smallest inner diameter (4 ) is 0.2-4 of the smallest internal diameters (9).

In a submersible pipe, according to a useful model, the nozzle (13) in the position of the inner diameter (OOippe of the nozzle has an outer diameter (Uosche) of the nozzle, which is smaller than the sum of the inner diameter (Oiteg) of the nozzle and the four smallest inner diameters (4).

In a submersible pipe, according to a useful model, the outer diameter of the nozzle is (OoshessOipten-aha), and the inner diameter (Oippeuu of the nozzle is 1.2-8 of the smallest internal diameters (a).

The submersible pipe, according to a useful model, is designed to be used in a cyclone to separate solid particles and/or at least one liquid from the gas stream.

Here, to remove the gas flow from the cyclone, the downpipe has a gas inlet and a gas outlet. During operation, gas enters the submersible pipe through the inlet for

From the gas and again exits the submersible pipe through the gas outlet. Thus, a gas flow is created inside the downpipe from the gas inlet in the direction of the gas outlet.

In addition, the downpipe, according to the useful model, has a first section that is designed as a nozzle. This nozzle has on one side an inner diameter of the nozzle, and this diameter of the nozzle in the direction of the flow and thence in the direction of the outlet for the gas is reduced to the smallest inner diameter.

In addition, the submersible pipe has a second section through which gas flows after the first section during operation. This section is designed as a diffuser, and the diffuser on its side, which is the far side in relation to the first section, has the inner diameter of the diffuser. The inner diameter of the diffuser decreases from there in the direction of the first section to the smallest inner diameter.

The nozzle is characterized by the shape of the lateral surface in the form of a truncated cone. Such a side surface is rotationally symmetric about an axis that is the axis of symmetry of a truncated cone. The angle of the cone of this side surface with respect to the axis can be between 1" and 88", in particular between 15" and 65".

This design of the tapered nozzle makes its production particularly simple and therefore very cost-effective. Moreover, this design reduces the pressure drop, which is especially important for the separation of solid particles due to the relatively large gas flow.

Thus, the cross-section of the downpipe through which the gas flows becomes smaller as it tapers, starting from the cross-section defined by the inner diameter of the nozzle to the smallest cross-section defined by the smallest inner diameter.

Starting from this narrowing of the downpipe, the downpipe expands again in the direction of the gas flow to a larger cross-section, which is defined by the inside diameter of the diffuser.

To separate the particles from the gas when the particles are the dispersed phase, the gas outlet of the cyclone must be properly designed in relation to its diameter to avoid high pressure losses while maintaining the primary function of vortex stabilization and separation efficiency. This does not apply to hydrocyclones, which separate gas from liquid with a higher density, where the gas phase is a continuous phase and is much smaller relative to the flow volume.

Thus, the cyclone discharge nozzle can be accordingly designed with either a much smaller diameter or a rapidly decreasing diameter in the discharge nozzle (e.g. exponentially, not linearly) from a very high angle inlet nozzle shape to the mid-axis (funnel shape or the shape is similar to Laval's nozzle). This design can lead to moderate pressure losses due to the very small volume of the gas flow, since it is a dispersed phase. On the other hand, hydrocyclones sometimes require additional devices at the vortex inlet (such as impinger plates) to avoid denser fluid entering the vortex inlet. Such devices are not required for cyclones that separate particles from gas. In fact, such devices would be disadvantageous, as particles would have the opportunity to interact with them, which could lead to more particle destruction (for example, due to particle collisions). In addition, a non-linear decrease in the diameter of the vortex nozzle should increase the pressure loss for cyclones that separate solids from gas, since the volume of gas is much greater than the volumetric flow of particles.

In a preferred embodiment of the utility model, the inner diameter of the nozzle can be 1.2-8 times larger, in particular 1.4-2.88 times larger, than the smallest inner diameter. In addition, in a preferred embodiment, the length of the nozzle extending from the section with the inner diameter of the nozzle to the section with the smallest inner diameter can be 0.4-4.0 of the smallest inner diameter. Otherwise, the length follows from the selected angle and inner diameter. With this form, a very strong effect can be achieved according to a useful model, in which even in the case of moderate pressure losses throughout the cyclone, a very high separation efficiency is achieved.

In the next preferred embodiment of the utility model, the nozzle may have, in the position of the nozzle inner diameter, an outer nozzle diameter that is smaller than the sum of the nozzle inner diameter and 4 times the smallest inner diameter (UoschensOippegn4x). In other words, at the end of the nozzle, that is, in the position characterized by the inner diameter of the nozzle, there is a ring, the width of which is smaller than the 4 smallest inner diameters ("4x(y). Such a ring with these dimensions is used, in particular, for a nozzle that has the shape of the side surface of a truncated cone. With the help of such a ring, a simple way of approximating the shape of the downpipe to the shape of the Laval nozzle can be realized. Such a ring is suitable for further additional adjustments, for example, the downpipe can

To be adjusted to the changed operating parameters.

In an additional preferred embodiment of the utility model, the outer diameter of the nozzle can be less than the sum of the inner diameter of the nozzle and the 4 smallest inner diameters (OochessOippennach), and the inner diameter of the nozzle can be 1.2-8 of the smallest inner diameters. It is especially desirable that the outer diameter of the nozzle could be smaller than the sum of the inner diameter of the nozzle and 0.25 of the smallest inner diameter (UoschdenyeO;ippe--0.25ha), and the inner diameter of the nozzle could be equal to 1.4-2.85 of the smallest inner diameter. In addition, this shape is characterized by the shape of the ring, which is located at the end of the nozzle, that is, in the position of the inner diameter of the nozzle. This design is also used for a nozzle that has the appearance of a sonic nozzle. We should add that with the help of a ring of this shape, it is possible to influence the flow of gas through the submersible tube in a very simple way.

In the preferred embodiment of the useful model, the diffuser has the design of the lateral surface of a truncated cone or cylinder, respectively. With this shape, the diffuser is rotationally symmetric with an axis, namely the axis of symmetry of a truncated cone or cylinder, respectively. In this case, the cone angle between the side surface and the axis is between 0" and 457, preferably 37-15". The axis of symmetry of the truncated cone or cylinder, respectively, is also the axis of symmetry of the diffuser and may also be the axis of symmetry of the nozzle. Since the diffuser is often a particularly large structural element, such a particularly simple diffuser design can provide significant cost savings.

In an additional preferred embodiment of the utility model, a connecting cylinder can be installed between the nozzle and the diffuser. The connecting cylinder connects the nozzle at the point where it has the smallest internal diameter to the point of the diffuser where it has the smallest internal diameter. Therefore, the connecting cylinder at the joint has an inner diameter of the joint, which is identical to the smallest inner diameter. The length of the connecting cylinder or truncated cone, respectively, which extends from the nozzle to the diffuser, is preferably less than 8 of the smallest internal diameters (I «8ha). The connecting cylinder has an extremely simple shape, which provides a smoother passage from the diffuser to the nozzle. Thus, the flow through the downtube can be further improved and, therefore, a reduction in pressure loss can be achieved. In addition, it is possible that the connecting cylinder from the nozzle to the diffuser has a different thickness, providing a better connection between the nozzle and the diffuser in terms of construction and resistance to wear or any deformations, for example due to the different thickness of the nozzle and the diffuser or the cylinder itself, as as a rule, the cylinder profile is a biconvex, biconcave, plano-convex or plano-concave curvilinear profile.

An additional embodiment relates to ensuring the flow direction in front of the nozzle and/or after the diffuser by at least one additional nozzle or additional diffuser, respectively. The design, consisting of several convergent nozzles, which are installed next to each other, is simple and their production costs are small. Several nozzles and/or diffusers, which are installed next to each other, ensure high adaptability of the submersible pipe to operational parameters. In the case of such a design, the radius of curvature can vary in the longitudinal direction of the nozzle, and the smallest radius of curvature is at the place of greatest curvature.

In an additional preferred embodiment, the junction between the nozzle and the diffuser and/or only the nozzles and/or diffusers is smoothed. The joint can be, for example, polished. Due to this smoothness, it is possible to avoid a negative effect on the behavior of the gas flow. When a connecting cylinder is installed between the nozzle and the diffuser, for the same reason it is preferable that the connection between the connecting cylinder and the nozzle and/or the connection between the connecting cylinder and the diffuser is smoothed, for example by polishing .

In an additional preferred embodiment, at least one part of the submersible pipe, such as the negative profile of the nozzle, the connecting cylinder and/or the diffuser, consists of one mounting part or several mounting parts, respectively. To reduce the weight of assemblies, they can be designed as hollow bodies. In other words, the downpipe has such inwardly turned mounting parts formed by the negative profile of the nozzle, connecting cylinder and/or diffuser. Such a shape is rotationally symmetric with an axis, namely the axis of symmetry of the negative profile. Since the weight of the mounting parts is often lower than steel, a reduction in weight and/or a sufficiently simple design, for example for anchoring a buried pipe, provides a significant cost reduction. Therefore, this provides a fairly simple way to improve cyclones and/or submersibles in operational installations without major construction work.

In principle, it is desirable to make at least part of the buried pipe for use

With a model of heat-resistant and/or erosion-resistant materials, such as ceramic fiber materials, carbon fibers, etc., and/or, optionally, it is desirable to provide their surface with a coating that resists erosion.

Next, the utility model is explained by way of example embodiments with reference to the figures. Here, all the described and/or displayed features independently or in any combination form the subject of a useful model, regardless of their concise statement in the formula or their backlinks.

Fig. 1 schematically shows the design of the cyclone,

Fig. 2a - schematically shows the buried pipe,

Fig. 265 - schematically shows a buried pipe with a connecting part,

Fig. For - schematically shows a buried pipe with applied corners,

Fig. 35 - schematically shows a nozzle with a ring,

Fig. 4 - schematically shows a submersible pipe with an applied diffuser corner,

Fig. 5a - shows the location of the submersible pipe in the cyclone,

Fig. 50. - an additional variant of the location of the submersible pipe in the cyclone is shown,

Fig. 5c - an additional variant of the location of the submersible pipe in the cyclone is shown,

Fig. 5a - shows an additional variant of the location of the submersible pipe in the cyclone,

Fig. ba - shows the location of the immersion tube with the cylinder on the housing cover,

Fig. 66. - shows an additional version of the location of the immersion pipe with a cylinder on the housing cover,

Fig. bs - an additional variant of the location of the immersion pipe with a cylinder on the housing cover is shown,

Fig. ba - the location of several submersible pipes in the cylinder is shown,

Fig. 7a - shows the symmetrical arrangement of buried pipes,

Fig. 76 - shows the asymmetric arrangement of buried pipes,

Fig. va - shows a cyclone with a symmetrically located submersible pipe, and

Fig. 8r - shows a cyclone with an eccentrically located submersible pipe.

The basic design of cyclone 1, which is used to remove solid particles or liquids from the gas stream, is schematically shown in Fig. 1. Cyclone 1 consists of a body 3, which has a cylindrical section 5 and a narrowing section or a conical section 6. In the cylindrical section 5 60, there is a channel 4 for supplying gas, through which a gas stream can be introduced together with particles. Cyclone 1, as a rule, has such an arrangement of parts that the conical part 6 is directed downwards in the direction of the gravity field. In its lowest place, the discharge device 7 is located, through which the particles and/or liquid separated from the gas stream can be unloaded.

During operation, the gas flow together with the particles is introduced into the housing C through the gas supply device 4. This, as a rule, is realized with tangential orientation so that the circular movement of the gas flow is directly created. The gas stream moves from the gas supply device 4 in the direction of the conical section 6 in the form of a spiral. Due to centrifugal forces, the particles move towards the outer wall of the cyclone 1 and there they move towards the exhaust device 7 under the influence of gravity. Then the gas enters the downpipe 2 through the gas inlet 8 when moving up, and the purified gas leaves it through the gas outlet 9.

In Fig. 2a shows the basic design of the submersible pipe 2 with the diffuser 12 on the second section 11 and the nozzle 13 on the first section 10, connected to each other at the connection point 14. The nozzle 13 has a wide opening with an inner diameter Oippeig and a narrow hole with a small inner diameter a.

The diffuser in the place 14 of the connection with the nozzle 13 is also characterized by the smallest inner diameter 4, and in the direction of its other end, its diameter again increases to a larger inner diameter.

In Fig. 265 shows the basic design of the submersible pipe 2, which consists of a diffuser 12, a nozzle 13 and a connecting part 15, which is connected to the diffuser 12 and nozzle 13 at the connection point 14. The connecting part 15 is characterized by a diameter that corresponds to the smallest internal diameter and.

The gas inlet 8 (Fig. 2a and 25) of the downpipe coincides with the end of the nozzle 13 and/or with the position of the inner diameter of the nozzle. But it doesn't have to be. Most likely, it is also possible that an additional element is located in the nozzle, such as, for example, a cylinder, and one of its ends, instead of a nozzle, forms an inlet for gas.

In Fig. According to the shown submersible pipe 2 from Fig. 2a with the applied dimensions. At the junction between the diffuser 12 and the nozzle 13, the submersible pipe is characterized by the smallest internal diameter a. The nozzle 13 is made in the form of the side surface of a truncated cone, and in the version shown by dashed lines, it can have a length or height H. The nozzle 13, which is

Zo is quite flat, i.e. short and has less height, shown by the continuous line. The truncated cone nozzle has an axis of symmetry 20, and the truncated cone is rotationally symmetric with respect to this axis 20. In addition, for the variant shown in dashed lines, the truncated cone nozzle has a small cone angle "a". In the variant shown by the solid line, the cone angle is greater.

In Fig. 35 shows only the nozzle 13, in which an additional ring 18 is located at its end.

Given this ring 18, the nozzle 13 has an inner diameter O;lpeg at the end and an outer diameter

Bosheg, which is enlarged due to ring 18.

In fig. 4 shows the buried pipe 2 in fig. 2a with the applied angle B of the diffuser cone 12.

The diffuser 12 of the submersible pipe 2 is made in the form of a truncated cone and has an axis 21 of rotation.

In Fig. 5a - 5a show different depths of insertion of the submersible pipe 2 in the housing C of the cyclone.

In Fig. Ba submersible pipe 2 is located in such a way that it completely protrudes inside the body C in such a way that the gas inlet 8 of the submersible pipe 2 is located below the lower edge of the gas supply channel 4. The gas inlet 8 of the submersible pipe 2 is inside the housing 3.

In Fig. 55, the submersible pipe 2 only partially protrudes inside the body C so that the gas inlet 8 of the submersible pipe 2 is located at the same height as the lower edge of the gas supply channel 4.

In Fig. 5c shows an option in which only about half of the submersible pipe 2 protrudes into the body C so that the gas inlet 8 of the submersible pipe 2 is located above the lower edge of the channel 4 for gas supply.

In Fig. 5a, the entire submersible pipe 2 is located outside the housing 3. From the outside, the submersible pipe 2 is located so that the gas inlet 8 is directly on the cover 17 of the housing 3.

Figure 5b shows the submersible pipe 2, which is completely covered by the cylinder 19. This cylinder and the submersible pipe are located on the cover 17 of the housing 3. In each of the figures ba-6j, only part of the housing C with the cover 17 is shown. In this case, the part below the cover 17 is the internal part of the case. Therefore, the cylinder and the immersion pipe 2 completely protrude inside the housing 3.

In Fig. 6p shows a variant of implementation in which the submersible pipe 2 only partially protrudes inside the housing C so that the gas outlet 9 of the submersible pipe 2 is located outside the body 3, and the gas inlet 8 is located inside the housing 3. The cylinder 19 is completely located inside body C and protrudes beyond the depth pipe 2 into the body 3.

In Fig. bs shows an embodiment in which the submersible pipe 2 is mounted outside the housing C directly on the cover 17. The cylinder 19 is in the same position on the opposite side of the submersible pipe 2 inside the housing 3.

In Fig. b shows a top view of the cover 17 with the arrangement of several submersible pipes 2, and in the lower field is shown a side view of the same arrangement with the submersible pipes 2, which together are completely located in the cylinder 19 inside the body 3. The location of the submersible pipes can be varied as indicated above, see Fig. 6 years and BS.

In Fig. 7a shows the location of several submersible pipes in the housing C of the cyclone 1, which are located on the cover 17 of the housing C of the cyclone 1. In this case, the location of the submersible pipes 2 is symmetrical with the axis of symmetry, which passes through the submersible pipe 2 in the center.

In Fig. 76 shows the arrangement in fig. 7a with two additional submersible pipes 2, which are located asymmetrically. In addition, Fig. 75 shows that the submersible pipe 2, which is located in the center, does not completely protrude into the housing C of the cyclone 1, thus some submersible pipes can be located at different heights relative to the gas inlet of the nozzle.

Fig. va and 8p illustrate the difference between the central location and the eccentric location of the submersible pipe 2. In Fig. two submersible pipes 2 are concentrically located relative to the cover 17, and in Fig. 85 submersible tube 2 is located outside the center. Therefore, it is an eccentrically located submersible pipe 2. In addition, in Fig. 865 direction and amount of eccentricity are indicated by arrows.

Example of implementation:

Working data:

The volume flow rate is 1 m3/s

The particle load is 0.1 kg/kg of gas

The average particle diameter is 10 μm

The concentration of particles is 2600 kg/m Z

The density of gas at 307 C is 1.189 kg/m3

Dynamic air viscosity at 30 "C / 18.4x106 Pa s (1.84x105 kg/m s

Zoo inlet temperature

Inlet pressure 1.033x105 Pa (1.033 bar)

Cyclone form:

The width of the inlet is 0.12 m

The height of the intake hole O, bm

The radius of the buried pipe is 0.15 m

The length of the buried pipe is 0.45 m

The radius of the cyclone is 0.45 mm

The length of the cyclone is 2.25 mm

The length of the cylindrical part is 0.9 m

The radius of the output device is 0 15 m

Design of the Veho VehOA nozzle

The inner diameter of the nozzle is 0.075m 0105m

The inner diameter of the diffuser is 0.075 m. 0.105 m

The smallest inner diameter is 0.04 m 0.059 m

The length of the nozzle is 0.04 m 0.04 m

The length of the diffuser is 04 m 0.7 m

The length of the connecting cylinder is 0.01 m 0.01 m

The speed in the narrowing is 214 m/s 100 m/s

Result:

Separation efficiency n - 96 90 (traditional) and » 96 95 expected in the preferred embodiment of the useful model -22x102 Pa (22 mbar) (traditional) and, «

DR pressure loss: 25x102 Pa (25 mbar) at 100 m/s expected in the preferred embodiment of the useful model

Coo)

List of designations 1 cyclone 2 submersible pipe

C housing 4 gas supply channel 5 cylindrical section 6 conical section 7 exhaust device 8 gas inlet 9 gas outlet 10 first part 11 second part 12 diffuser 13 nozzle 14 connection point 15 connecting part 17 cover 18 ring 19 cylinder 20 axis of symmetry of the nozzle 21 axis of symmetry of the diffuser and the smallest inner diameter

Oitpeg inner diameter of the nozzle

Oomsheg the outer diameter of the nozzle

H is the height of the nozzle

Claims (5)

USEFUL MODEL FORMULA 1. Submersible pipe (2) for removing gas from the cyclone (1), in which gas during operation enters the submersible pipe (2) through the gas inlet (8) and exits through the gas outlet (9), which is characterized by the fact that the submersible pipe (2) has a first part (10) designed as a nozzle (13) that tapers from the inner diameter (Juippeg) of the nozzle to the smallest inner diameter (a), and a second part (11) along which during operation, gas flows after the first part (10) and is designed as a diffuser (12), which narrows from the inner diameter of the diffuser in the direction of the first part to the smallest inner diameter (4), and because the nozzle (13) has the shape of a side surface , rotationally symmetrical with the axis (20), in the form of a truncated cone, and the angle (co) of the cone between the side surface and the axis (20) is 157-657. 2. Submersible pipe according to claim 1, which differs in that the inner diameter (Yulpei) of the nozzle (13) is 1.2-8 of the smallest inner diameter (4), and also in that the length (H) of the nozzle (13) is greater than the inner diameter (Juipple) of the nozzle to the smallest inner diameter (4) is 0.2-4 of the smallest inner diameter (a). 3. A submersible pipe according to any one of the preceding points, characterized in that the nozzle (13) in the position of the inner diameter (Ogpeg) of the nozzle has an outer diameter (Uosheg) of the nozzle, which is smaller than the sum of the inner diameter (Ole) of the nozzle and the four smallest internal diameters (4). 4. A submersible pipe according to any one of the previous items, which differs in that the outer diameter of the nozzle is (OoshchdesOhiptegnikha), and the inner diameter (ЮОиппег) of the nozzle is 1.2-8 of the smallest internal diameters (4). 5. A submersible pipe according to any one of the preceding points, which is characterized by the fact that it is made with the possibility of using it in a cyclone to separate solid particles and/or at least one liquid from the gas stream.