WO2007108720A1

WO2007108720A1 - Radial fan (variants)

Info

Publication number: WO2007108720A1
Application number: PCT/RU2007/000127
Authority: WO
Inventors: Viacheslav Georgievitch Karadzhi; Youri Georgievitch Moskovko
Original assignee: Balakirev, Evgeni Borisovitch
Priority date: 2006-03-21
Filing date: 2007-03-15
Publication date: 2007-09-27

Abstract

The group of inventions relates to radial fans provided with a spiral body. In the first and third variants of the fan, the plate (12) of a whirl damper having a height hw=Hw/D=0.10-0.12 is mounted on the external surface (9) of a collector (4) between meridional planes passing across the base line of the entire unfolding of the body (1) and at 45 degrees from said plane towards a tongue (14). In the second and fourth variants, the body (1) is provided with a plate (15) which has a height hw=Hw/D=0.10-0.14 and is arranged in front of blades (8) between meridional planes passing across the base line of the maximum unfolding of the body (1) and the tip (16) of the tongue (14). In the third and fourth variants, the blades are provided with a slat (19) located between the area, where the blades are jointed to the surface of a front disc (7) and the axis of rotation (13) of a rotor wheel and,in the projection on a plane perpendicular to the axis of rotation of the rotor wheel, a straight line connecting the axis (13) and the tip (22) of the slat does not go beyond a sector bounded by beams positioned in the range of ±0.05 of the angular pitch (t) of the blades with respect to the straight line connecting the axis (13) and the tie point (23) where the front edge (20) of the next in the rotation direction blade (8A) is jointed to the surface of the front disc (7)

Description

RADIAL FAN (OPTIONS)

Technical field

The group of inventions relates to radial fans in a 5 spiral casing.

The prior art.

In the prior art, radial fans with a guiding apparatus made in the form of a vortex damper at the south entrance to the impeller are known.

In the description of the invention “Central fan)), protected by RF patent N ° 2132970, IPC F04D 17/08, priority date 21.01.1998, publication date 10.07.1999 year, [1], there is a radial fan containing a spiral case equipped with

15 language, an impeller installed in the housing on the shaft with backward-curved blades and with a conical cover disc, an inlet manifold with sections of a curved profile in a meridional section, the outer surface of which forms an annular gap with the inner surface of the cover disc at the inlet of the impeller,

20 vortex suppressor, made in the form of at least one plate placed on the outside of the inlet manifold in front of the annular gap in the zone of the greatest opening of the casing, the outlet pipe, equal in width to the casing of the fan.

In the description of the invention "Central fan)),

25 protected by RF patent JNk 2215195, IPC F04D 17/08, priority 04/27/2002, publication date 10/27/2003, [2] a radial fan is presented, comprising a spiral case, an impeller mounted on the shaft with the impeller curved back blades and with a conical cover disk, an inlet manifold with sections of a curved profile in a meridional section, the outer surface of which forms an annular gap with the inner surface of the cover disk at the entrance to the impeller,

5 a vortex suppressor made in the form of at least one plate placed on the outside of the inlet manifold in front of the annular gap in the zone of the greatest opening of the casing, the outlet pipe is equal in width to the casing of the fan, and the width of the casing L is 0.9 ... 1 , 1 of the diameter D of the impeller, the input manifold contains a cylindrical section, the length of the input manifold L _in is 0.48 ... 0.63 of the diameter D of the impeller, and the diameter of the inlet D _B χ in the impeller is 0.66 ... 0.69 impeller diameter D.

Placing the vortex suppressor plate in the inventions [1, 2] in the zone

15 of the largest opening of the casing provides high aerodynamic characteristics of the fan, however, studies have shown the possibility of improving them.

The radial fan presented in the description of the invention [2], adopted for the closest analogue of the 1st and 2nd options

20 inventions.

In the description of the utility model “Radial fan”, protected by RF patent N ° 54112, IPC F04D 17/08, priority 27.12.2005, publication date 10.06.2006, [3], there is a radial fan containing a spiral case equipped with

25 language, an impeller installed in the housing on the shaft with backward-curved blades and with a conical cover disk, an inlet manifold with sections of a curved profile in a diametric section, the outer surface of which forms an annular gap with the inner surface of the cover disk at the entrance to the impeller, an outlet pipe, the width of which is equal to the width of the spiral case, a vortex suppressor made in the form of at least one plate placed on the outside of the suction pipe in front of the annular gap between the planes passing through the axis of rotation of the impeller, one of which intersects the line of maximum opening of the case, and the other is located at an angle of 45 degrees, in the direction of the tongue of the spiral casing.

Placing the vortex suppressor plate in the utility model [3] in the zone of the greatest distance of the impeller from the spiral section of the casing provides high aerodynamic characteristics of the fan, however, studies have shown the possibility of improving the aerodynamic characteristics of the fan and reducing the acoustic noise of the fan at the inlet.

The radial fan, presented in the description of the utility model [3], is taken as the closest analogue of the 3rd and 4th variants of the invention.

Disclosure of embodiments of the invention

Solved technical problem is to increase the efficiency of the fan.

The technical result of the 1st and 2nd fan options is to increase the pressure characteristics and efficiency of the fan in the working area.

The technical result of the 3rd and 4th fan options is to increase the pressure characteristics and efficiency of the fan in the working area while reducing the sound power at the fan inlet at the blade frequency and its harmonics. The solution of the technical problem is provided when performing the objects of the group of inventions with the following set of features essential for the objects of the group of inventions to achieve the claimed technical results.

The radial fan according to the 1st embodiment, as in the closest analogue [2], contains a spiral casing equipped with a tongue, an impeller mounted on the shaft on the shaft with backward curved blades and with a conical cover disc, an inlet manifold with sections of a curved profile in the meridional cross-section, the outer surface of which forms with the inner surface of the front disk at the entrance to the impeller an annular gap, a vortex damper made in the form of at least one plate placed on the outside of the input the vector in front of the annular gap in the zone of the greatest opening of the spiral casing, the outlet pipe, but unlike the closest analogue [2], the vortex suppressor plate is located between two meridional planes, one of which crosses the line of the greatest opening of the casing, and the other is located at an angle of 45 degrees, from it to the side of the tongue of the spiral case, while the height of the vortex suppressor plate is 0.10 ... 0.12 of the diameter of the impeller.

The radial fan according to the 1st embodiment is characterized in that the width of the outlet pipe is equal to the width of the spiral casing, which is 0.9 ... 1.1 of the diameter of the impeller, the inlet manifold contains a cylindrical section, the length of the inlet manifold is 0.48 ... 0 , 63 of the diameter of the impeller, and the diameter of the entrance to the impeller is 0.66 ... 0.69 of the diameter of the impeller. In this case, the outer edge of at least one vortex suppressor plate is in contact with the outer surface of the inlet manifold.

In addition, at least one eddy absorber plate in a diametric section is located at an angle of ± 10 degrees to the input manifold, counting from the meridional direction towards the direction of rotation of the impeller, and at an angle of ± 10 degrees to a plane passing through the axis of rotation of the impeller .

The radial fan according to the 1st embodiment is characterized in that at least one plate of the vortex suppressor is made flat.

The radial fan according to the 2nd variant, as in the closest analogue [2], contains a spiral casing equipped with a tongue, an impeller installed in the casing on the shaft with backward curved blades and with a conical front disk, an input manifold with sections of a curved profile in the meridional cross-section, the outer surface of which forms with the inner surface of the cover disk at the entrance to the impeller an annular gap, a vortex suppressor made in the form of at least one plate placed on the outer side of the input call in front of the annular gap in the zone of the greatest opening of the spiral casing, the outlet pipe, but unlike the closest analogue [2], the radial fan is equipped with a plate mounted on the wall of the tapering part of the spiral casing opposite the impeller blades between two meridional planes intersecting respectively the line of the largest the disclosure of the spiral casing and the toe of the tongue of the spiral casing in the tapering part of the spiral casing adjacent to the line of greatest b

the opening of the housing, while the height of the plate is 0.10 ... 0.14 of the diameter of the impeller.

The radial fan according to the 2nd embodiment is characterized in that the plate on the wall of the spiral casing is installed at an angle of 70 ± 5 degrees to the axis of rotation of the impeller.

The radial fan according to the 2nd embodiment is characterized in that at least one plate mounted in a spiral casing is made flat.

The radial fan according to the 2nd embodiment is characterized in that the vortex suppressor plate is located between the passing meridional planes, one of which crosses the line of greatest opening of the casing, and the other is located at an angle of 45 degrees, towards the tongue of the spiral casing, while the height of the vortex suppressor plate is 0, 10 ... 0.12 impeller diameters. The radial fan according to the 2nd embodiment is characterized in that the width of the outlet pipe is equal to the width of the spiral casing, comprising 0.9 ... 1.1 of the diameter of the impeller, the inlet manifold contains a cylindrical section, the length of the inlet manifold is 0.48 ... 0 , 63 of the diameter of the impeller, and the diameter of the entrance to the impeller is 0.66 ... 0.69 of the diameter of the impeller.

At the same time, at least one eddy absorber plate in the meridional section is located at an angle of ± 10 degrees to the input manifold, counting from the radial direction towards the direction of rotation of the impeller, and at an angle of ± 10 degrees to the plane passing through the axis of rotation of the impeller .

The radial fan according to the 2nd embodiment is characterized in that at least one vortex suppressor plate is made flat.

The radial fan according to the 3rd option, as in the closest analogue [3], contains a spiral case equipped with tongue mounted on the shaft of the impeller with backward curved blades and with a conical front disk, an inlet manifold with sections of a curved profile in diametric section, the outer surface of which forms an annular gap, an outlet pipe, a vortex suppressor with the inner surface of the cover disk at the inlet of the impeller made in the form of at least one plate placed on the outside of the inlet manifold in front of the annular gap between the planes passing through the axis of rotation of the impeller and, one of which crosses the line of greatest opening of the housing, and the other is located at an angle of 45 degrees, in the direction of the tongue of the spiral housing, but unlike the closest analogue [3], the height of the indicated vortex suppressor plate is 0.10 ... 0.12 the diameter of the impeller, and each blade of the radial impeller is made with a slat located between the blade contacting the surface of the front disk and the axis of rotation of the impeller, while in a projection onto a plane perpendicular to the axis of rotation of the impeller, a straight line connecting schaya impeller rotation axis and the sock slat, without departing from the sector bounded by beams arranged in a range ± 0,05 angular pitch of the blades relative to the straight line connecting the impeller rotational axis and the point of abutment of the leading edge of the blade during the next rotation to the front surface of the disk

The radial fan according to the 3rd option is characterized in that the width of the outlet pipe is equal to the width of the spiral casing, comprising 0.9 ... 1.1 of the diameter of the impeller, the inlet manifold contains a cylindrical section, the length of the inlet manifold is 0.48 ... 0 , 63 of the diameter of the impeller, and the diameter of the entrance to the impeller is 0.66 ... 0.69 of the diameter of the impeller. At the same time, at least one eddy absorber plate in the diametric section is located at an angle of ± 10 degrees to the input manifold, counting from the meridional direction towards the direction of rotation of the impeller, and at an angle of ± 10 degrees to the plane passing through the axis of rotation of the impeller .

The radial fan according to the 4th embodiment, as in the closest analogue [3], contains a spiral casing equipped with a tongue, an impeller installed in the casing on the shaft with backward curved blades and with a conical front disk, an input manifold with sections of a curved profile in diameter cross-section, the outer surface of which forms with the inner surface of the cover disk at the entrance to the impeller an annular gap, an outlet pipe, a vortex suppressor made in the form of at least one plate placed with the outer casing ony of the input manifold in front of the annular gap between the planes passing through the axis of rotation of the impeller, one of which crosses the line of maximum opening of the housing, and the other is located under the corner 45 degrees, towards the tongue of the spiral housing, but in contrast to the closest analogue [3], the radial the fan is equipped with a plate mounted on the wall of the spiral casing opposite the impeller blades between two meridional planes intersecting, respectively, the line of greatest opening of the spiral casing the tongue toe of the spiral casing, in the tapering part of the spiral casing adjacent to the line of maximum opening of the casing, and each blade of the radial impeller is made with a slat located between the contact of the blade to the surface of the front disk and the axis of rotation of the impeller, while projecting onto a plane perpendicular the axis of rotation of the impeller, a straight line connecting the axis of rotation the impeller and the slat nose does not extend beyond the sector limited by beams located in the range of ± 0.05 of the angular pitch of the blades relative to the straight line connecting the axis of rotation of the impeller and the abutment point of the leading edge of the blade following the rotation of the blade to the surface of the front disk.

The radial fan according to the 4th embodiment is characterized in that the plate on the wall of the spiral casing is installed at an angle of 70 ± 5 degrees to the axis of rotation of the impeller, and the plate height is 0.10 ... 0.14 of the diameter of the impeller. The radial fan according to the 4th embodiment is characterized in that the vortex suppressor plate is located between the meridional planes, one of which crosses the line of greatest opening of the casing, and the other is located at an angle of 45 degrees, towards the tongue of the spiral casing, while the height of the vortex suppressor plate is 0.10 ... 0.12 impeller diameters.

The radial fan according to the 4th embodiment is characterized in that the width of the outlet pipe is equal to the width of the spiral casing, comprising 0.9 ... 1.1 of the diameter of the impeller, the inlet manifold contains a cylindrical section, the length of the inlet manifold is 0.48 ... 0 , 63 of the diameter of the impeller, and the diameter of the entrance to the impeller is 0.66 ... 0.69 of the diameter of the impeller.

Brief description of figures with drawings. In the following, the invention is explained in a detailed description of embodiments of a radial fan with reference to the accompanying drawings, in which:

Fig. 1 shows a fan in a plan view. Figure 2 shows a section A-A in figure l of the fan according to the 1st and 2nd variants of execution.

FIG. 3 shows a section A-A in FIG. 1 of the fan according to the 3rd and 4th embodiments.

In Fig.4 shows a section bB in Fig.Z. Figure 5 shows the remote element In figure 4.

Figure 6 shows a view of figure 5. In Fig.7 shows a view of D in Fig.5.

On Fig is a section E-E in Fig. 1 for the fan according to the 1st and 2nd variants of execution. Figure 9 shows a section E-E in figure l for the fan according to the 3rd and 4th variants of execution.

Figure 10 shows the remote element W in figure 2 and 3. Figure 1 shows a fragment of the impeller of the fan according to the 3rd and 4th variants of execution with the location of the blades in the zone of permissible deviations from the angular pitch.

In Fig L 2 shows the blade of the impeller of the fan according to the 3rd and 4th options when viewed from the side.

In Fig.13 shows a view And in Fig.11 when making the blades from a solid sheet. Ha Fig. 14 shows a view of And in Fig. Ll when performing a composite blade. On Fig presents a graph of the dependence of the coefficient of the total pressure of the fan from the installation angle of the vortex plate for the fan according to the 1st embodiment.

On Fig presents a graph of the dependence of the efficiency of the fan on the installation angle of the plate of the fan eddy suppressor according to the 1st embodiment.

On Fig presents a graph of the dependence of the coefficient of the total pressure of the fan from the height of the plate of the fan eddy suppressor according to the 1st and 3rd options for execution. On Fig presents a graph of the dependence of the efficiency of the fan on the height of the plate of the fan vortex suppressor according to the 1st and 3rd options for execution.

On Fig presents a graph of the dependence of the coefficient of the total pressure of the fan on the height of the plate in a spiral casing of the fan according to the 2nd and 4th options for execution.

On Fig presents a graph of the dependence of the efficiency of the fan on the height of the plate in a spiral casing of the fan according to the 2nd and 4th options for execution.

On Fig presents a comparison of the narrow-band noise spectrum at the suction of the fan according to 3 and 4 variants of execution and the fan adopted as the closest analogue.

On Fig presents a comparison of the sound power level at the input of the fan according to 3 and 4 variants of execution and the fan adopted as the closest analogue. On Fig shows the influence of the relative angular deviation of the slat on the difference in sound pressure ΔL on the blade frequency of the fan according to 3 and 4 variants of execution of both the fan and the fan adopted as the closest analogue. Best embodiments of the invention The radial fan in all 4 variants comprises a spiral case 1 (Figs. 1,2,3,4), an impeller 2 installed in it, the shaft 3 of which is kinematically connected with an electric drive, for example, with an electric motor (in Fig. . not designated), the input manifold 4 with a curved profile in the diametrical section, and the output pipe 5 (Fig.1,2,3,4). The impeller 2 includes a main 6 and a cover 7 discs and blades 8 installed between them. Between the outer surface 9 of the inlet manifold 4 (FIG. 5), the cover disc 7 and the walls of the housing 1, a circulation chamber 10 is formed (FIG. 4).

At the entrance to the impeller 2, an annular gap 11 is formed between the inner surface of the cover disk 7 and the outer surface 9 of the input manifold 4 (Fig. 5,6). A circumference on the outside of the inlet manifold 4 is a vortex suppressor made in the form of at least one plate 12 (Figs. 4,5,6,7).

According to the 1st and 3rd embodiments of the radial fan, as shown in FIG. 4, one of the vortex suppressor plates, for example, the plate 12, is installed in the sector between the conditional meridional planes (i.e., planes passing through the axis 13 rotation of the impeller 2), one of the planes (Pl. A, Fig. 8,9) crosses the line of greatest opening of the spiral casing 1, and the other (Pl. B, Fig. 8,9) is located at an angle of 45 degrees, towards the tongue 14 of the spiral casing 1 (in the coordinate system in Fig. 8,9, S _B = 0 ...- 45 degrees). The inner edge of the vortex suppressor plate 12 is connected to the surface of the inlet manifold 4 (Fig. 5.7). The relative height h _{in the} vortex plate 12 is equal to the ratio of the height H _{in the} vortex plate 12 to the diameter D of the impeller 2 (equal to the diameter of the circle described the ends of the blades 8) is:

The swirl plate 12 in diametric section can be installed at an angle a _of -0 ± L0 degrees, to the input manifold 4 with a count towards the direction of rotation of the impeller 2 (Fig.6) and at an angle βb – H0 degrees, relative to the axis of rotation of the impeller 2 (Fig. 7), and the outer edge of the plate 12 can be made both rectilinear (Figs. 5, 6, 7) and curved (not shown in Fig.).

In accordance with the 2nd and 4th options, the radial fan is equipped with a plate 15 mounted on the wall of the spiral case 1 opposite the blades 8 of the impeller 2 in the tapering part of the spiral case 1 adjacent to the line of maximum opening of the case, between the conditional meridional planes, one of which passes through the sock 16 of the tongue 14 of the spiral casing 1 (Pl. B, Fig. 2,3), and the other (Pl. A, Fig. 2,3) crosses the line of greatest opening of the spiral casing 1 (Fig. 1,2,3) ) In this case, the relative height h _C p of the plate 15, equal to the ratio of the height H _C p of the plate 15 to the diameter D of the impeller 2 (figure 10), is:

The plate 15 is installed at an acute angle γ _C p to the axis of rotation of the impeller (Fig. 1), and can be performed with a rectilinear or arbitrary shape of the outer and side edges, with a flat or complex surface. With a variable width of the plate 15 (for example, with a rectilinear outer edge), the height H _C p is taken in its middle part (Fig. 10). The length of the plate 15 can vary within wide limits, however, as a rule, does not exceed the width H of the blades 8 of the impeller 2.

In the 3rd and 4th versions of the radial fan, each blade 8 of the impeller 2 contains a main section 17 (Fig. 4,11,12), the front edge 18 (Fig. 12) of which is adjacent to the front disk 7, and a section located closer to the axis of rotation of the impeller 13, hereinafter referred to as the “pre-stitch” 19 (FIGS. 4, 11, 12). The main section 17 and the slat 19 can be made as a whole, for example, from a sheet of metal (Fig. 12,13) or in the form of an aerodynamic profile (not shown in Fig.), Or composite (Fig. 14) by attaching the slat 19 to the main part 17 of the blade 8. The leading edge 20 of the slat 17 can be located in a range of angles of ± 10 degrees to a plane perpendicular to the axis of rotation 13 of the impeller 2, and the lateral edge 21 is at an acute angle to the leading edge 20 (Fig. 4.12 ), and are interconnected by a smooth curve, for example, by an arc of a circle, forming a sock 22 ancestor ylka 19 (Figure 12). The leading edge 20 of the slat 19 is made curved, for example, along an arc of a circle projected onto a plane perpendicular to the axis of rotation 13 of the impeller 2 (Fig. 4.12), and its side edge 21 may be curved, for example, increasing with increasing distance from leading edge 18 local radius R _BC (Fig). The surface of the slat 19 can be made in the form of a surface with smooth contours, in particular a cylindrical one (Fig .ll), or with a steep slat 19 and the main section 17 of the blade 8 (not shown in Fig.). In a projection onto a plane perpendicular to the axis of rotation of the impeller 13, the straight line connecting the axis of rotation of the impeller 13 and the nose 22 of the slat 19 does not extend beyond the sector limited by rays located in the range Δt = ± 0.05 of the angular pitch t of the blades 8 relative to the straight line connecting the rotational axis 13 of the impeller 2 and the abutment point 23 of the leading edge 20 of the next blade 8A in the direction of rotation with the front disc 7 (Fig. ll). In this case, the point on the toe 22 through which the straight line passes is determined when the slat 19 is tangent to the toe 22 and is parallel to the axis 13 of the impeller 2, and the value the angular step t is equal to 2πrad divided by the number of blades N in the impeller: t = 2l / N.

The main section 17 of the blade 8 fans in the 3rd and 4th options, as well as the blade 8 fans in the 1st and 2nd options can be performed with a curved, for example, a cylindrical surface, and with a flat surface. When performing the main section 17 of the blades 8 with a flat surface, its front edge 18 can be made straightforward (Fig. 12). In this case, the front disk 7 at the abutment section of the blade 8 (Fig. 4) is a hyperbolic surface, the generatrix of which is the rectilinear front edge 18 of the main section 17 of the blade 8.

To ensure the rigidity of the slats 19 of the blades 8, if necessary, the lateral edges 20 of the slat 19 are connected by a ring 24 (figure 4). Similar rings can be installed at the ends 25 (fi.4) of the blades 8 in addition to the already installed ring 24 on the lateral edges 20 of the slat 19 (not shown in Fig.).

As noted above, in accordance with the 3rd embodiment of the radial fan, the relative height h _{in the} vortex plate 12 is equal to the ratio of the height H _{in the} vortex plate 12 to the diameter D of the impeller 2: h _in = H _in / D = 0.10 ... 0.12. Plate 12 vihregasitelya in diametric section can be mounted _in an angle a = + 10 °, to the inlet manifold 4 with a count toward the rotational direction of the impeller 2 (Figure 6) and at an angle β _a = ± 10 °, with respect to the axis of rotation 13 of the impeller 2 (Fig. 7), and the outer edge of the plate 12 can be made both rectilinear (Fig. 5) and curvilinear (not shown in Fig.). An example of a preferred embodiment of radial fan options.

In a preferred embodiment, the radial fan according to the 1st embodiment comprises one flat eddy absorber plate 12, which is in contact with the outer surface 9 of the inlet manifold 4 and is set at angles a _at = 0 degrees, and β _at -0 degrees, the input manifold 4 is made with a cylindrical insert 26, the length L _{inx of the} inlet manifold 4 is 0.48 ... 0.63 of the diameter D of the impeller 2, the diameter D _{inx of the} suction pipe 4 at the entrance to the impeller 2 is 0.66 ... 0.69 of the diameter D impeller 2, the width H of the blades 8 of the impeller 2 is equal to at least 0.35 diameter D p the working wheel 2, the width of the outlet pipe 5 is equal to the width L of the spiral casing 1 of the fan and is 0.9 ... 1.1 of the diameter D of the impeller 2: L _x = (0.48 ... 0.63) D; D _bx = (0.66 ... 0.69) D; H≥0.35D; L = (0, 9 ... 1,1) J ⁾ - (Fig. 1,4).

In a preferred embodiment of the fan according to the 2nd embodiment, a plate 15 is additionally installed at an angle γ _C c = 70 ± 10 degrees, to the axis 13 of rotation of the impeller 2 (Fig. I) ₅ located closer to the meridional plane of Pl. B (Fig. 2) passing through the sock 16 of the tongue 14 of the spiral housing 1.

In a preferred embodiment of the radial fan according to the 3rd and 4th options, the impeller 2 of the radial fan (Fig. 3,4) contains 13 blades 8, the width H of the blades 8, equal to the distance between the front 7 and the main 6 disks at the exit of the impeller 2, is 0.25 ... 0.37 of the diameter of the impeller D. The main section 17 of the blades 3 is made flat, and the slat 19 adjacent to it in a section perpendicular to the axis of rotation 13 of the impeller 2, in the form of an arc of a circle, the front 20 and the lateral 21 edges of the slat 19 are connected in a circle, and the lateral edge 21 made with a local radius R _BK equal to at least 0.5 D near the front edge 20 and parallel to the axis of rotation 13 of the impeller 2 (i.e. equal to infinity) near the main disk 6 (Fig.12). In a projection onto a plane perpendicular to the axis of rotation of the impeller 2, the straight line connecting the axis of rotation of the impeller 2 and the nose 22 of the slat 19 does not extend beyond the sector limited by beams located in the range At = ± 0.05t relative to the straight line connecting the axis 13 of the rotation of the impeller 2 and the abutment point 23 of the leading edge 20 of the next 8 A blade with the front disk 7 (Fig. 11). The front 7 and main 6 discs can be made with an increased diameter equal to (1,1 ... 1,2) D and (1,05 ... 1,1 S) D, respectively, with the formation in the meridional section between the generatrices of the front 7 and the main 6 disks in the direction from the axis of rotation 13 to the ends 25 of the blades 8 of the impeller 2 of the non-expanding channel (not shown in Fig.).

In this case, the fan according to the 3rd variant contains one flat plate 12 of the vortex suppressor with a height of Hb-0.10 ... 0.12 of the diameter D of the impeller 2, the plate 12 is in contact with the outer surface 9 of the inlet manifold 4 and installed at angles CXg = ¹ O hail, and βв ⁼ 0 hail. (Fig. 6,7), the inlet manifold 4 is made with a cylindrical insert 26, the length L _{inx of the} inlet manifold 4 is 0.48 ... 0.63 of the diameter D of the impeller 2, the diameter Din of the suction pipe 4 at the entrance to the impeller 2 equal to 0.66 ... 0.69 of the diameter D of the impeller 2, the width H of the blades 8 of the impeller 2 is equal to at least 0.35 of the diameter D of the impeller 2, the width of the outlet pipe 5 is equal to the width L of the spiral casing 1 of the fan and is 0, 9 ... 1,1 of the diameter D of the impeller 2: L _in = = (0.48 ... 0.63) D; D _c) g (0.66 ... 0.69) D; H≥0.35D; L = (0.9 ... 1, l) D, H ₃ = (0, 10 ... 0.12 D)

(Fig. 1.4).

In the fan according to the 4th embodiment, a plate 15 is additionally installed at an angle γsp = 70 ± 10 degrees, to the axis of rotation of the impeller 2 (Fig. 1) and is located closer to the meridional plane HL B (Fig. 3) passing through the toe 16 of the tongue 14 of the spiral casing 1, and the height of the plate 15 is Ha] = (O) IO ... 0.14) D.

The group of inventions operates as follows. When the impeller 2 rotates in the circulation chamber 10, a swirling toroidal (vortex) flow occurs. The installation of a vortex suppressor containing at least one plate 12 in the area of exit from the spiral casing provides braking of the toroidal (vortex) flow, which is accompanied by an increase in pressure in the circulation chamber 10 in front of the annular gap 11 (Fig. 4,5). As a result of the pressure difference in the circulation chamber 10 and at the entrance to the impeller 2, an annular jet is blown onto the inner surface of the cover disk 7 through the annular gap 11, which increases the momentum of the jet formed in the annular gap 11. This creates an additional vacuum on the inner surface of the cover disk 7 , reducing the intensity of the vortex, and, therefore, reducing aerodynamic losses not only at the entrance to the impeller 2, but also the fan as a whole.

The dependence of the total pressure coefficient

and coefficient of efficiency (efficiency) ηv of the fan at constant values of the coefficient of performance φ = 4Q / II> ² u (where Q is the capacity of the fan, P _v is the total pressure, D is the diameter of the impeller 2 of the fan, and is the peripheral speed of the ends of the blades 8 impeller 2 fans, p - air density) from the installation site of the vortex-suppressor plate 12, obtained in experiments with the fan according to the 1st and 3rd options, is presented in FIG. 15 and FIG. 6, respectively. In accordance with the graphs in FIGS. 15, 16 in the range of angles δ _{in the} installation the swirl plate 12 from 0 deg, to 45 deg, in the direction of the tongue 14 (in the coordinate system shown in Figs. 8 and 9, the positive value of the angles δ _{in is} counted from Pl. A towards the narrowing of the housing 1, therefore, the range of angles δ _in is δ _in = 0 ...- 45 deg.) The maxima of the total pressure coefficient ψ and the efficiency η _in . With an increase in the fan performance coefficient φ, the maxima become more pronounced, and as we approach the boundary of the specified range of angles δ _{, the} moduli of the derivatives dψ / dδ _in and dη / dδ _in decrease. A change in the relative height h _{in the} swirl plate 12, as shown in FIGS. 17 and 18, also affects the total pressure ψ and the efficiency η _{in the} fan, with a maximum in the range h _in = 0.10 ... 0.12.

This, most likely, is associated with the braking of the air involved in the movement during the rotation of the front disk 7, and arising behind the plate 12 of the stagnant zone. At a low height h, sufficient inhibition of the circulation flow is not provided _{in the} plate 12, which reduces the momentum of the jet formed in the circumferential gap 11. At a high height of the plate 12, a braking zone arises in front of it in the region of the maximum opening of the spiral of the housing 1, as a result of which it is blown into the ring air jet, which increases the momentum of the jet flowing to the surface of the front disk 7, and the height h _{in the} plate 12 has quite clearly defined values at which the maximum coefficient ψ and efficiency η _c . Further the increase in the height of the plate 12, apparently, violates the toroidal (vortex) flow, which leads to a deterioration in the aerodynamic characteristics of the radial fan. This confirms the significance of the feature relating to the selected boundaries of the height h _in = H _B / D of the vortex suppressor plate 12.

When performing plate 12 curved aerodynamic losses are less than when performing plate 12 flat. The angles a _in , β _{in the} installation of the curved plate 12 and the channel profile in the circumferential gap 11 should be optimized depending on the parameters and operating conditions of the fan. However, the coupling of the plate 12 with the outer surface 9 of the inlet manifold 4 has a complex spatial contour, which complicates the manufacturing technology of the guide apparatus of the centrifugal fan.

The implementation of the plate 12 flat with an edge in contact with the outer surface 9 of the inlet manifold 4, and the location of the plate 12 along the generatrix in the diametrical section of the inlet manifold 4 at an angle a _in = ± 10 degrees, towards the direction of rotation of the impeller 2 ensures the manufacturability of the eddy current suppressor and whole. The placement of the plate 12 at an angle β _in = ± 10 degrees, due to a decrease in the accuracy of the connection of the plate 12 with the outer surface 9 of the input manifold 4, and has little effect on the technical result.

The total pressure coefficient ψ and efficiency η _{in the} fan, made according to the 2nd and 4th options, when the relative height h _C p = Hcp / D changes, the plates 15 also have a maximum (Fig. L 9 and Fig. 20). The presence of the plate 15 contributes to a more uniform distribution of the velocity field in the output manifold 5 by the direction of the flow to the side of the wall of the spiral casing 1. When the plate 15 is closer to the outlet 5 from the meridional plane of Pl. A, a sufficient uniformity of the velocity field is not achieved, as when the plate 15 is located in the direction of narrowing of the spiral casing 1 from the meridional plane of Pl. B.

The implementation of the input manifold 4 with a length Lв ^ г ⁼ (0.48 ... 0.63) D due to the cylindrical section 26 with the diameter of the entrance to the impeller 2 equal

provides increased uniformity of the flow entering the impeller 2, which delays the separation of the boundary layer from the surface of the cover disk 7 and from the blades 8 of the impeller 2 during its rotation. As a result, it is possible to increase the width H of the blades 8 to 0.35 and above the diameter D of the impeller 2: H≥0.35D. This makes it possible to increase the width L of the casing to L = (0.9 ... 1, l) D, as a result of which the static pressure of the outgoing flow increases in all variants of the fan with their preferred embodiment. The implementation of the outlet pipe 5 and the spiral housing 1 of the same width L simplifies the manufacturing technology of the fan. Radial fans made according to the 3rd and 4th options (marked in light tone), as shown in Fig. 21, have lower values of sound pressure at the blade frequency and its harmonics in comparison with the fan adopted as the closest analogue [3] (indicated by a dark tone). As a result, the sound power levels at the input of the 3rd and 4th variants of the radial fan (indicated by a light tone), as shown in Fig. 22, are reduced in comparison with the sound power levels of the fan adopted as the closest analogue [3] (indicated by in a dark tone). Moreover, it was experimentally established that at the relative deviation Δt of the position of the nose 22 of the slat 19 of the blade 8 of the impeller 2 from the angular step / sound pressure difference ΔL _B at the blade frequency of the claimed fan L (f) _in and the fan is the closest analogue [3] L _B. _A , reaches, as shown in FIG. 23, the maximum values modulo (which corresponds to the minimum noise at the fan inlet).

Industrial applicability The variants of radial fans in a spiral case described in the description can be manufactured at any specialized enterprise. The implementation of the 1st and 2nd variants of the invention ensures the achievement of the claimed technical result, namely, an increase in the pressure characteristic and the efficiency of the fan in the working area. The implementation of the 3rd and 4th variants of the invention provides, in addition to increasing the pressure characteristic and the efficiency of the fan in the working area, also reducing the sound power at the fan inlet at the blade frequency and its harmonics. Thus, the presented variants of the invention are aimed at solving the technical problem, namely, to increase the efficiency of the fan. The parameters of the vortex suppressor made in the form of a plate 12, the dimensions of the circumferential gap 11, as well as the parameters and installation location of the plate 15 in the spiral casing 1 can be optimized in the indicated angle ranges depending on the operating conditions and characteristics of the fan. LIST OF POSITIONS AND DESIGNATIONS FOR DESCRIPTION

GROUPS OF INVENTIONS "RADIAL FAN (BAPAHT)"

1 - spiral case;

2 - impeller;

3 - shaft drive, for example an electric motor;

4 - input collector;

5 - output pipe; 6 - the main disk;

7 - front disk;

8 - the blade of the impeller 2;

9 - the outer surface of the inlet manifold 4;

10 - circulation chamber; 11 - annular clearance;

12 - vortex suppressor plate mounted on the outer surface 9 of the inlet manifold 4 in the zone of greatest opening of the housing 1;

13 - axis of rotation of the impeller 2;

14 - the language of the spiral casing 1; 15 - plate mounted on a spiral casing 1 in the zone of its greatest disclosure;

16 - the toe of the tongue 14 of the spiral housing 1;

17 - the main section of the blades 8,

18 - the front edge of the main section 15 of the blades 8, adjacent to the front disk 7;

19 - slat - section of the blade 8, located closer to the axis 13 of rotation of the impeller 2;

20 - the leading edge of the slat 19;

21 - the lateral edge of the slat 19; 22 - toe slat 19;

23 - the abutment point of the leading edge 20 of the next along the rotation of the blade 8A to the front disk 7;

24 - a ring connecting the side edges 21 of the slats 19 of the blades 8;

25 - the output edge of the blades 8 of the impeller 2;

26 is a cylindrical section of the inlet manifold 4.

Pl.A - meridional plane passing through the axis of rotation 13 of the impeller 2 and crossing the line of greatest disclosure of the spiral housing 1;

Pl. B - meridional plane passing through the axis of rotation 13 of the impeller 2 and located at an angle of 45 degrees to the meridional plane of Pl. A towards the tongue 14 of the spiral housing 1; Pl.B - meridional plane passing through the axis of rotation 13 of the impeller 2 and the sock 16 of the tongue 14 of the spiral housing 1; δ _{in the} angle of installation of the plate 12 of the vortex suppressor; a _in - the angle of inclination of the plate 12 of the vortex suppressor to the input manifold 4 with a countdown towards the direction of rotation of the impeller 2; βB - the angle of inclination of the plate 12 of the vortex suppressor to the axis of rotation 13 of the impeller 2;

Uel - the angle of inclination of the plate 15 to the axis 13 of rotation of the impeller 2; Lin - length of the input manifold 4; D is the diameter of the impeller 2; D _Bx - diameter of the inlet manifold 4 at the entrance to the impeller 2; H- impeller width 2; L is the width of the housing 1 of the fan; H _in - the height of the plate 12 of the vortex suppressor. H sp - the height of the plate 15 mounted on the wall of the spiral housing 1. h _in ~ Hv / D - the relative height of the plate 12 of the vortex suppressor.

- the relative height of the plate 15 mounted on the wall of the spiral casing 1. η _in - the efficiency of the fan (efficiency); ψ = 2P _v / pu ² - coefficient of total pressure of the fan; φ = 4Q / πD ² u - fan performance coefficient; Q - fan performance; Py is the total pressure of the fan; and - peripheral speed of the ends of the blades 8 of the impeller 2 of the fan; p is the density of air. t = 2π / N is the angular pitch of the blades 8 of the impeller 2, equal to 2π rad, divided by the number of blades N in the impeller; At is the angle in the projection onto a plane perpendicular to the axis of rotation of the impeller 2, between the straight connecting axis 13 of the rotation of the impeller 2 with the point 23 of the abutment of the blades 8 of the impeller 2 to the surface of the front disk 7, and connecting the axis of rotation of the impeller 2 with the toe 22 slat 19;

ΔL = L (f) _in -L _in . _A is the difference in sound pressure at the blade frequency at the input of the claimed fan L (f) _in and the fan is the closest analogue [3], L, _B- l

Claims

THE INVENTION GROUP FORMULA

1. A radial fan, comprising a spiral casing (1), equipped with a tongue (14), mounted in the casing (1) on the shaft (3), the impeller (2) with backward curved blades (8) and with a conical

5 by the front disk (7), the inlet manifold (4) with sections of a curved profile in the meridional section, the outer surface (9) of which forms with the inner surface of the front disk (7) at the entrance to the impeller (2) an annular gap (11), a vortex suppressor made in the form of at least one plate u (12) located on the outside of the inlet manifold (4) in front of the annular gap (11) in the zone of greatest opening of the spiral housing (1), the outlet pipe (5), characterized in that the vortex suppressor plate (12) is located between the two meridion planes, one of which crosses the line of the greatest

15 of the housing opening (Pl. A), and the other (Pl. B) is located at an angle of 45 degrees, from it towards the tongue (14) of the spiral casing (1), while the height of the indicated plate (12) of the eddy suppressor is 0.10. ..0.12 diameter of the impeller (2).

2. A radial fan according to claim 1, characterized in that 20 the width of the outlet pipe (5) is equal to the width (L) of the spiral casing

(1) component 0.9 ... 1.1 of the diameter (D) of the impeller (2), the inlet manifold (4) contains a cylindrical section (26), the length (Lβ _X ) of the inlet manifold (4) is 0.48 ... 0.63 of the diameter (D) of the impeller (2), and the diameter (D in) of the entrance to the impeller (2) is 0.66 ... 0.69 25 of the diameter (D) of the impeller (2).

3. A radial fan according to claim 1 or claim 2, characterized in that the outer edge of at least one plate (12) of the vortex suppressor is in contact with the outer surface (9) of the inlet manifold (4).

4. Radial fan according p.l or claim 2, characterized in that at least one plate (12) vihregasitelya in meridian section is angled _at a = ± 10 °, to the inlet collector (4) with a count of radial direction towards

5 of the rotation of the impeller (2), and at an angle / З _в = ± 10 deg, to the plane passing through the axis (13) of rotation of the impeller (2).

5. A radial fan according to claim 1 or claim 2, characterized in that at least one plate (12) of the vortex suppressor is made flat. v 6. Radial fan, comprising a spiral casing (1), equipped with a tongue (14), mounted in the casing (1) on the shaft (3), the impeller (2) with backward curved blades (3) and with a conical front disk (7) , input manifold (4) with sections of curved profile in the meridional section, external

15 surface (9) which forms with the inner surface of the front disc (7) at the entrance to the impeller (2) an annular gap (11), a vortex suppressor made in the form of at least one plate (12) located on the outside of the input the collector (4) in front of the annular gap (11) in the zone of the greatest opening of the spiral

20 of the housing (1), the outlet pipe (5), characterized in that the radial fan is equipped with a plate (15) mounted on the wall of the spiral housing (1) opposite the blades (8) of the impeller (2) between two meridional planes intersecting the line, respectively greatest disclosure of the spiral casing

25 (Sq. A) and sock (16) of the tongue (14) of the spiral casing (1) (Pl. B), in the tapering part of the spiral casing (1) adjacent to the line of maximum opening of the casing (1), while the height (H £) of the plate (15) is 0.10 ... 0.14 of the diameter (D) of the impeller (2).

7. The radial fan according to claim 6, characterized in that the plate (15) on the wall of the spiral casing (1) is installed at an angle of USp = 70 ± 10 degrees to the axis (13) of the rotation of the impeller (2).

8. A radial fan according to claim 6 or claim 7, characterized in that 5, at least one plate (15) installed in the spiral casing (1) is made flat.

9. A radial fan according to claim 6, characterized in that the vortex suppressor plate (12) is located between the planes passing through the axis of rotation of the impeller (2), one of which crosses the line of maximum opening of the housing (1) (Pl. A ), and the other (Pl. B) is located at an angle of 45 degrees, in the direction of the tongue (14) of the spiral case (1), while the height (Nsp) of the vortex suppressor plate (12) is 0.10 ... 0.16 diameter ( D) impeller (2).

10. A radial fan according to claim 6 or claim 7 or claim 9, 15, characterized in that the width of the outlet pipe (5) is equal to the width

(L) of the spiral case (I) _{5 of a} component of 0.9 ... 1.1 diameter (D) of the impeller (2), the input manifold (4) contains a cylindrical section (26), the length (L _B χ) of the input manifold ( 4) is 0.48 ... 0.63 of the diameter (D) of the impeller (2), and the diameter (L _B χ) of the entrance to the impeller 20 (2) is 0.66 ... 0.69 of the diameter (D ) impeller (2).

11. The radial fan according to claim 9, characterized in that at least one plate (12) of the vortex suppressor in the meridional section is located at an angle a _in = ± 10 degrees to the input manifold (4) with a count from the radial direction towards the direction

25 rotation of the impeller (2), and at an angle β _in = ± 10 degrees, to a plane passing through the axis (13) of rotation of the impeller (2).

12. A radial fan according to claim 9, characterized in that at least one plate (12) of the vortex suppressor is made flat.

13. A radial fan, comprising a spiral housing (1) equipped with a tongue (14), mounted in the housing (1) on the shaft (3), the impeller (2) with backward-curved blades (8) and with a conical front disk (7), input manifold (4) with sections

5 curved profile in diametric section, the outer surface (9) of which forms with the inner surface of the front disk (7) at the entrance to the impeller (2) a circumferential gap (11), an outlet pipe (5), a vortex suppressor made in the form of at least at least one plate (12) located on the outer side of the input manifold (4) in front of the annular gap (11) between the planes passing through the axis of rotation of the impeller (2), one of which intersects the line of maximum opening of the housing (1) (Pl. A), and the other (Pl. B) is located at an angle of 45 degrees, side tongue (14) of the spiral body (1), wherein

15 in that the height (H _in ) of said vortex suppressor plate (12) is 0.10 ... 0.12 of the diameter (D) of the impeller (2), and each blade (8) of the impeller (2) is made with a slat ( 19), located between the junction (23) of the blade (8) to the surface of the front disk (7) and the axis (13) of rotation of the impeller (2), while in projection on

20 the plane perpendicular to the axis of rotation of the impeller (2), the straight line connecting the axis of rotation of the impeller (2) (2) and the toe (22) of the slat (19) does not extend beyond the sector limited by beams located in the range ± 0.05 angular pitch (/) of the blades (8) relative to the straight line connecting the axis of rotation of the impeller (13)

25 (2) and the abutment point (23) of the leading edge (20) of the blade following the direction of rotation of the blade (8A) to the surface of the front disk (7).

14. The radial fan according to claim 13, characterized in that the width of the outlet pipe (5) is equal to the width (Z,) of the spiral casing (1) of 0.9 ... 1.1 of the diameter (D) of the impeller (2) input the collector (4) contains a cylindrical section (26), the length (Lin) of the input manifold (4) is 0.48 ... 0.63 of the diameter (D) of the impeller (2), and the diameter of the inlet (D _B χ) into the working the wheel (2) is 0.66 ... 0.69 of the diameter (D) of the impeller (2).

5 15. The radial fan according to item 13 or 14, characterized in that at least one plate (12) of the vortex suppressor in the meridional section is located at an angle a _in = ± 10 degrees to the input manifold (4) with a readout from the radial direction towards the direction of rotation of the impeller (2), and at an angle v deg, to a plane passing through the axis (13) of rotation of the impeller (2).

16. A radial fan, comprising a spiral casing (1), equipped with a tongue (14), mounted in the casing (1) on the shaft (3), the impeller (2) with backward curved blades (8) and with a conical

15 by the front disk (7), the inlet manifold (4) with sections of a curved profile in a diametrical section, the outer surface (9) of which forms a circumferential gap (11) at the entrance to the impeller (2), the outlet a nozzle (5) whose width is equal to the width (L)

20 of the spiral case (1), the vortex suppressor, made in the form of at least one plate (12), placed on the outside of the inlet manifold (4) in front of the annular gap (11) between the rotation of the impeller (2) passing through the axis (13) ) planes, one of which (Pl. A) crosses the line of greatest

25 disclosure of the housing (1), and the other (Pl. B) is located at an angle of 45 degrees. towards the tongue (14) of the spiral casing (1), characterized in that the radial fan is equipped with a plate (15) mounted on the wall of the spiral casing (1) opposite the blades (8) of the impeller (2) between two meridional planes intersecting respectively, the line of the greatest opening of the spiral case (1) (Pl. A) and the toe (16) of the tongue (14) of the spiral case (1), in the tapering part of the spiral case (1) adjacent to the line of the greatest opening of the case (1), while the height (H _C p) of the plate (15) is

5 0.10 ... 0.14 diameters (D) of the impeller (2), and each blade (8) of the impeller (2) is made with a slat (19) located between the adjoining (23) of the blade (8) to the surface the front disk (7) and the axis (13) of the rotation of the impeller (2), while in the projection onto a plane perpendicular to the axis (13) of rotation of the impeller (2), ι is a straight line connecting the axis (13) of rotation of the impeller (2) and the toe (22) of the slat (19) does not extend beyond the sector limited by beams located in the range of ± 0.05 of the angular pitch (t) of the blades (8) relative to the straight line connecting the rotation axis (13) of the working th wheel (2) and the junction point (23) of the front edge (20) of the next downstream

15 rotation of the blade (8A) to the surface of the front disc (7).

17. A radial fan according to claim 16, characterized in that the plate (15) on the wall of the spiral casing (1) is installed at an angle γ _C p = 70 ± 10 degrees to the axis (130 of rotation of the impeller (2).

18. A radial fan according to claim 16 or 17, characterized in that at least one plate (15) installed in the spiral casing (1) is made flat.

19. A radial fan according to claim 16, characterized in that the height (H _B ) of the vortex suppressor plate (12) is 0.10 ... 0.12 of the diameter (D) of the impeller (2).

25 20. Radial fan according to item 16 or item 17 or item 19, characterized in that the width of the outlet pipe (5) is equal to the width (L) of the spiral case (1), which is 0.9 ... 1.1 diameters (D) the impeller (2), the input manifold (4) contains a cylindrical section (26), the length (L _B χ) of the input manifold (4) is 0.48 ... 0.63 the diameter (D) of the impeller (2), and the diameter (Din) of the entrance to the impeller (2) is 0.66 ... 0.69 of the diameter (D) of the impeller.

21. The radial fan according to claim 19, characterized in that at least one plate (12) of the vortex suppressor in the meridional section is located at an angle a _in = ± 10 degrees to the input manifold (4) counting from the radial direction towards the direction of rotation the impeller (2), and at an angle βv = ± 10 degrees to the plane passing through the axis (13) of rotation of the impeller (2).