JPS5925100A - Axial-flow blower - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION This invention relates to air blowing technology, and in particular to axial blowers (single-stage, two-stage, and multi-stage blowers).

This invention can be applied to Q@flow blower design for ventilation and has stable pressure characteristics within a wide range of air or delivery gas.

Trickle blast ridges have a wide range of industrial applications. A factor preventing wider openings is the occurrence of stall artifacts around the rotor blades, which result in pressure drops and pressure oscillations at low speeds of the air or delivery gas.

llI flow/K[
(see L1%S, Pat, rV & 13189260) is known, and it is a stepped case with an inlet and an outlet part, the diameter of the outlet part is smaller than the diameter of the interrogator part, and the inlet part has a stall flow. The ferrule is housed so as to form an annular passageway between the case and the ferrule for bypassing air flow. Guide vanes are provided in the ferrule. The lead-out portion of the case accommodates a rotor with a set of blades, the front tips of which are provided in the lead-in portion of the housing.

However, in this known blower, the annular passage extends too much in the axial direction, which increases the axial length of the blower.

Furthermore, the guide vanes provided in the seven errules to straighten the stall flow increase the hydrodynamic resistance at the inlet of the case in front of the rotor, reducing the pressure and efficiency of the wind armpit.

Also, the housing includes a ferrule that forms, together with the housing, an annular passage in which guide vanes for rectifying the flow are fixed inside, and a plurality of 'li1's are installed in the leading-out portion of the housing!
7) IGI consisting of a crotch housing with an introduction part
k, ventilation- is known (e.g. the West
German Magazine H, D, 1 (en
asler, NeueAxialventilator
en ohne 1nstablen BeL
r1e-bsbereich, V G B Kraf
twerkstechnik, 57 Jahrgan
g, H'eft 3. Mjirz 1 977.
5eiten 159 bis 165).

In these blowers, the O stall flow at the outlet from the annular passage particularly blocks the inlet and thus impedes the passage of the main flow into the flow path region in front of the rotor blades. Therefore, the pressure of all the delivery air and the flow in the stall area is relatively low, resulting in unstable operation.

Furthermore, trickle blowers essentially similar to those described above with guide vanes in the annular passage are known (the Pamp
hlet of%Licenaintorg//'kG
eneral-purpose Axial-flo
w fan /', Moscow US SR).

The inlet pipe is fixed to the casing part of the blower, and the inlet pipe has a basically large diameter in the outlet part of the case, and the guide vanes provided in the annular passage are arranged in the axial direction of the ferrule. Limited by length.

By using the inlet pipe, the inflow of the main air into the feeder Jgl can be improved to some extent. However, because the axial length of the guide vanes is limited, the stall flow tends to maintain a vortex that matches the rotational direction of the rotor, and the flow path in front of the rotor blades stabilizes the main flow of air. obstruct the passage. This reduces blower pressure and operational stability in stall flow conditions.

In view of the foregoing, the use of guide vanes in the annular passage in known axial flow blowers does not allow pressure optimization in stall flow conditions.

The present invention provides a trickle blower with guide vanes structured to increase pressure and efficiency in stall flow conditions and ensure stable blower operation over the operating range of air delivery from zero to maximum. Pointing to 1.

(a stepped housing consisting of an inlet portion and an outlet portion), the outlet portion having an inner diameter smaller than the inner diameter of the inlet portion; The lead-out part of the housing is connected to the lead-in pipe and houses a rotor having vanes arranged such that the tip is located in the lead-in part of the housing, and the seven errules are coaxial with the housing and spaced a certain distance from the lead-in pipe. This is achieved by means of a flow-through Klfi, which is provided at one side and forms an annular chamber with an inlet passage on the rotor side and an outlet passage in the inlet tube area, with guide vanes firmly fixed between them. (2) According to the invention, the tail portion of the guide vane reaches the introduction tube, and the portion between the introduction tube top ferrule and zero is curved in the direction of neutral force so as to form an annular lattice in the direction of neutral force.

Preferably, < means that the tail of each guide vane is at −45° from the neutral force direction.
It deviates from the "P" force direction over a range from +45 to +45.
The deflection of the guide device in this way optimizes the pressure at low delivery speeds of the air blower.

Note that the ratio of the width of each guide RQ to the width of the introduction passage of the annular chamber is between 2.0 and 3.0. The ratio of the width of the guide vanes to the width of the outlet passage of the annular chamber is 1.4 to 1.
．． The ratio between the height of the guide vane and its width is preferably between 0.4 and 0.65.

Such a ratio can reduce hydrodynamic losses while bypassing the stall flow through the annular chamber, thereby expanding the stable operating range and improving the operating efficiency of the blower at low air delivery speeds. .

Preferably, the ratio between the internal force of the inlet tube and the weight of the rotor including the ends of the blades is between 1.00 and 1.01.

Said ratio further improves the efficiency of the blower with said guide vanes.

As a note, the ratio between the 7 ferrules and the external force on the rotor blades is 1.01 to 1.05. provides a favorable path through the air to the rotor and improves the efficiency of the blower.

The axial blower of the present invention has a simple structure, but can expand the stable operating range and increase the pressure and efficiency.

The invention will now be described in more detail with reference to preferred specific embodiments in conjunction with the accompanying drawings.

Referring to FIG. 1, the axial blower according to the invention consists of a stepped housing 1 composed of two parts, the two parts being an inlet part 2 and an outlet part 3; The outlet part 3 has an inner diameter that is one size smaller than the introduction part 2 of the housing 1. An inlet tube 4 having a cubic capacity substantially equal to one cubic meter of the outlet part 3 of the housing 1 is connected to the inlet part-2.

The outlet part 3 of the housing 1 accommodates a rotor 5 with blades 5a.

The blade 5a is arranged so that its front tip 6 (FIG. 2) is located in the introduction part 2 of the /1 housing 10.

Distance SS b from the introduction pipe 4 of the receiving part 2 of the housing 1
//A ring 7 errule 7 is provided separately and coaxially with this. The ring 7 errule 7 and the introduction part 2 of the housing 1 define an annular (9) chamber 8 for bypassing the air loss a@% B11.

The annular chamber 8 for bypassing the stall flow S B// includes an introduction passage 8& provided between the vane 5a and the 7 errule 7, and an outlet passage provided between the 7 errule 7 and the introduction pipe 4. 8b. These communication paths 8a and gb have widths a and -b, respectively.

In this annular chamber, a guide vane 9 is located between the ferrule 7 and the introduction part 2 of the housing 1.
The tail VIvSIO of the guide vane 9 extends towards the inlet tube 4 and terminates therein. Between the ferrule 7 and the introduction tube 4, the tail 10 of the guide vane 9 is bent in the direction of neutral force, as clearly shown in FIGS. 3 and 4.
It forms an annular semi-circular lattice 11, a part of which is the fourth
It is indicated by dots in the figure.

The tail part 10 of the valley guide g9 is angled in the '+-+-inward direction,
Neutral force direction SS r// (Figure 4) from -45 to +4
5's 1st corner angle α7'? It's biased. The positive value of the angle αO corresponds to the deviation of the base 10 in the direction opposite to the direction of rotation of the blade 5aθ (10). These tails f! 1
vS10 is shown as a solid line in FIG. The negative @ of α in the angle corresponds to the deflection of the tail in the same direction as the rotational force direction % C// of the blade 5a, which is indicated by a dotted line.

In order to increase the pressure of the blast while the flow stalls, the stall flow leaves the annular passage 8 (FIG. 2) through the outlet passage 8b extending a distance %b between the ferrule 7 and the inlet tube 4. % B tt needs to spiral in the opposite direction to the rotor (1) blade 5a (2) rotational direction - C#. What is this?
The tails 10 of each guide vane 9 face the pressurized axial surface 13 (FIG. 3) of the rotor blades 5& by means of its concave side surface 12 (FIG. 4), and these tails 10 extend beyond 145 from the life direction %r〃. Due to the angle α deviation, the 0 guide gate stem 90 tail 10 can be observed. The rotating direction of the rotor blade 5a is directed in the direction opposite to CI, and the stall IJ11. 'B'' (Fig. 2) is forced in front of the rotor blade 5a (at 1υ) to the periphery of the through-flow section 14, thus
It is possible to promote the passage of the main current E〃 sucked in through the tube, and as a result, the pressure caused by the air flow can be increased.

In another embodiment of the blower according to the invention, if there is an outlet for reducing the blower N pressure in conditions where the flow stalls, the stalled flow escaping from the annular chamber 8 through the outlet passage 8b is transferred to the rotor 5. The blades 5a are oriented to match the rotational direction -CI. The stiffness is each guide wing 9 and the tail section 10a.
The concave side surface 12a (FIG. 4) faces the suction side surface 15 (FIG. 3) of the rotor blade 5a, and these tails 110
Angle α that a does not exceed -45 from the half-way direction XX r//
This can be achieved by being biased.

In order to swirl the stall fi'B' more effectively,
The tail 10, IQa (FIG. 4) with a concave side surface 12, 12& may project at its end 16 from the inner diameter of the ferrule 7 a certain length into the through-flow section 14 in the lifetime direction.

(1) Furthermore, the ratio between the width 1t of the guide g9 (Fig. 2) and the width u aI/ of the introduction passage 8a of the annular chamber 8, and the width % tlF and the width of the output passage 8b of the annular chamber 8. %I
The ratio between 61 and t/a = 2.0 to 3, respectively
．． Olt/b = 1.4-1.6, while the ratio between the guide vane 9 height % h tt and its @'&1 // is h/t = 0.4-0.65. be.

In order to improve the passage of the main stream %E (FIG. 2) to the rotor blades 5a, a collector 17 (FIG. 1) is provided inside the passenger pipe 4. For convenience, a container 18 is provided to remove the swirl of %F coming out of the rotor blades 5a.

Optimally, the inner diameter of the introduction pipe 4 (Fig. 2) is 1.00 to 1°0112 of the outer diameter D2 of the rotor blade 5a).
It's in the axle load.

When the ratio D1/L12 increases greatly by 1.00 to 1.01, the amount of air sucked through the passenger tube 4 increases by 5tt.
h'E obstructs the flow out from the annular passage 8b, and as a result, the performance of the air blower is affected.

A plane (
A preferred ratio is 1.01 to 1.05, which optimizes the passage of air through the page flow section 14 in front of the rotor blades 5a.

The axial blow limit of this invention operates as follows.

When the rotor 5 equipped with the blades 5a rotates in the direction indicated by %C, a sucked flow %Elf is generated and passes through the introduction pipe 4 and the penetrating light section 14, and passes between the blades 5a and the rectifier 618. The air supply gives pressure and air distribution in the duct 19 connected to the air exiting therefrom as essentially axial direction V)kiφF〃. As the resistance to flow increases within the duct 19, the density of air flow decreases with increasing pressure. At the delivery speed of air for the maximum pressure, the rotor blades 5
A flow stall occurs around a; the stalled flow %B1 is sent from the front tip by centrifugal force through the curved passage 8a to the multi-block passage 8, where @s C// (Fig. 3) The vortex is removed or rectified in the portion having the width -b#, and the vortex is generated so as to be deflected in the life direction and flow into the 'X flow section 14. Due to this vortex, the stalled current (14) BI/ is energized toward the periphery of the buying flow path section 14, and the pressure increases without preventing the mainstream % E /I from being sucked in, making it more stable. If the operating conditions are such that the pressure is increased at low delivery speeds, the tail 10 of the guide vane 9 is deflected over an angle α of +45 and the stall flow %B is in the annular chamber. 8 lead-out passage 8b
When passing through the rotor blades @5 & T7) rotation direction - CI
produces a vortex in the direction opposite to (Fig. 4), thereby creating a curved edge % of the coordinates of ψ-pressure and y-delivery rice in Fig. 5.
The pressure generated by the air blowing in the duct 19 can be increased, as indicated by d//.

In other applications of the blower, when the air delivery rate is low and the pressure is low, the tail 1i110a is deflected over an angle α of -45 from half 1% r//, so that the stall flow is diverted from the passage 8b. That's rotor blade 5 & 12J rotation direction%
A vortex is generated in the direction 20a that coincides with Ctt, and the pressure inside the duct 19 is applied as shown by the curve % g // in FIG.

(1f9 The curve S(f // shows the characteristic at low delivery speed when the tail of the guide vane is deflected at a relatively small angle from the radius -r.

The curve % g // shows the delivery salmon-pressure characteristics under stall flow conditions for a known axial blower.

The axial blower of the present invention fundamentally increases the efficiency of the blower under pressure, delivery, and stall flow conditions. Furthermore, delivery induced pressure characteristics at low air or gas delivery rates can vary depending on the conditions of use.

For applications requiring a high pressure in the duct 19, a two-stage or multi-stage modified version of the blower embodying the invention is used, each stage 21 (FIG. 6) and 22 being , is provided in the same manner as that described above with reference to the one-stage trickle air zone.

Inside the duct 23 v) Flow at maximum pressure As the resistance increases, Mt stalls around the vane 5a,
Each stage 21 and 22 is not affected by the annular neutral force direction υ grating 11 as previously described.
Stage and multi-stage fans operate similarly to single-stroke axial fans embodying this invention.

The modifications described so far of the one-stage and two-stage axial flow blower of the present invention, which consist of an annular chamber 8, a ferrule 7, and an annular mesolateral grid 11, expand the operating range,
It is possible to increase the pressure and make the operation of the blower more economical compared to similar known blowers, opening up even greater possibilities for industrial enclosures.

[Brief explanation of drawings]

FIG. 1 shows a schematic diagram of an axial blower according to the present invention. Second
The figure shows a detail of part A of FIG. 1 on an enlarged scale. FIG. 3 shows a cross section along the line segment group of FIG. 2. FIG. Figure 4 shows the cross section lTi1 along line segment 1v-bar in Figure 2.Figure 5 is a graph showing the relationship between pressure and delivery ratio. FIG. 6 shows a schematic diagram of a two-stage trickle blower of the present invention. 01: Housing 2: Inlet part (17) of housing 3: Outlet part of housing 4: Inlet pipe 5: Rotor 5
a: Vane 6: Front tip of vane 7: Ferrule 8: Annular chamber 8a: Introduction passage 8b: Output passage 9: Guide vane 10.1
0a: Tail part of guide wing 11: Half-way direction 12.12
Concave side surface 13 of the second guide a: Pressure side surface 14 of the blade 5a:
Through-flow section 15: Vane 5a ■ Suction side [16: Tail part of guide vane 17: Industrial fan 18: Adjuster 19: Duct 20:
Direction of the vortices of the stall flow opposing the rotational direction of the rotor 20a
: Rotor ■ Direction of vortex of stall flow that corresponds to IP1 rotation direction
21.22: Axial blower 6th inset 23: Duct a: Introductory passage 8a m b = width of 14 out 1i11++b r:
Medium force edge α: Touch k;, Ku, I: Feather 5a
Rotation direction E: Height of the guide h * Height of the guide decrease L: Guide - Q
Width F: Curve coming from rotor blade 5a Dl: Introductory pipe 4
Inner nJ straight weight D2: Outer straight weight of the rotor blade C: Width of a certain inner blade part d, , e, f, g: % Delivery lid - pressure Continued from page 1 Priority claim @February 2, 1983■Soviet Union (SU)■3
539801 0 Inventor Valery Prokovyevich Perederyi Soviet Union Donetsk Prospekt Dozerzhin Skogo 6 Kwarchila 88 0 Inventor Viktor Nikolayevich Morshanov Soviet Union Donetsk Prospekt Semashko 26 Kwarchila 42 573-

Claims (1)

[Scope of Claims] 1. Consists of a stepped housing (1) formed by an inlet part (2) and an outlet part (3), the outlet part (3)
has an inner diameter smaller than the inner diameter of the lead-in part (2), the lead-in part having an inner diameter essentially equal to the inner diameter of the lead-out part (3) of the housing (1);
The lead-out part (3) of the housing (1) has its front end (6) connected to the lead-in part (2) of the housing (1).
), the housing (1) is coaxial with the housing (1) and is located at a certain distance from the inlet pipe (4).
1) to form an annular chamber (8) having an inlet passage (8a) on the side of the rotor (5) and an outlet passage (8b) on the side of the inlet pipe (4).
In an axial blower in which the guide R (9) is fixed in the chamber (8) with its tail (10) facing the inlet pipe (4), the tail (10) of the guide X (9) It extends to the introduction pipe (4) and is curved in the semi-gloss direction at the part between the introduction pipe (4) and the ferrule (7), forming an annular semi-gloss lattice. Axial flow blower 2 characterized in that the tail (10 and 10a) of the guide x (9) is deflected from the semi-gloss direction over an angular variation α from -45 to +45. Axial ventilation according to paragraph 1 - the ratio between the width of the three guides jK (9) (4 and the width of the introduction passage (8a) of the annular chamber (8) is from 20 to 3.0, the guide vanes ( 9) width (4 and the width of the outlet passage (8b) (b)
) is between 1.4 and 1.6, the guide vane (9)
The ratio between the height h) and its width (4 is 0.4 or n
I according to claim 1, characterized in that: 65
The ratio of the inner diameter of the introduction pipe (4) to the diameter of the rotor (5) measured at the tip of the blade (5a) 10 is 1.00 to 1.
, 01, wherein the Q ratio between the diameter of the ferrule (7) and the outer diameter of the rotor blade (5a) is from 1.01 to 1.05. The axial flow blower according to item 1 of the scope of Tokken Takoyuki, characterized in that