KR101672265B1 - Mixed flow impeller having hollow airfoil blades - Google Patents

Abstract

[0001] The present invention relates to a structure of a hollow-blade cross-section jet impeller, and more particularly, to a structure of a hollow- The flow is smoothly transferred without generating peeling (vortex) between the vanes and the vanes, and the direction of discharge from the impeller discharge port is changed from the radial direction to the axial direction so that the flow energy is efficiently utilized and the operating efficiency of the impeller is increased, And the flow direction of the impeller can be smoothly changed in the axial direction by smoothly flowing the flow in the impeller flow path at the time of application, Thereby improving the efficiency of the axial flow type blower, changing the operating point, In order to reduce the noise generated from the impeller by improving the flow in the pulsator passage and to eliminate the structural risk of damage to the rotary shaft at the start of the impeller, To reduce the moment of inertia of the impeller.

Description

{MIXED FLOW IMPELLER HAVING HOLLOW AIRFOIL BLADES}

[0001] The present invention relates to a structure of a hollow-blade cross-section jet impeller, and more particularly, to a structure of a hollow- The flow is smoothly transferred without generating peeling (vortex) between the vanes and the vanes, and the direction of discharge from the impeller discharge port is changed from the radial direction to the axial direction so that the flow energy is efficiently utilized and the operating efficiency of the impeller is increased, And the flow direction of the impeller can be smoothly changed in the axial direction by smoothly flowing the flow in the impeller flow path at the time of application, Thereby improving the efficiency of the axial flow type blower, changing the operating point, In order to reduce the noise generated from the impeller by improving the flow in the pulsator passage and to eliminate the structural risk of damage to the rotary shaft at the start of the impeller, To reduce the moment of inertia of the impeller.

Generally, an impeller is a main part of a pump, a blower or a compressor. The impeller is rotated with several pulleys arranged at equal intervals on a circumference, and a gas or fluid such as air, water or oil is connected to a shaft Energy is created when flowing through the feathers.

Normally, the feathers are divided into a centrifugal type and an axial flow type, and the centrifugal type feathers flow in a direction perpendicular to the axis in which the fluid or gas is rotated, and the axial flow vortex flows in the axial direction of the axis in which the fluid or gas rotates.

Meanwhile, the above-mentioned impeller is used for conveying a fluid, and a conventional centrifugal impeller configured to be used for conveying a fluid is as follows.

FIG. 1 is a front perspective view of a conventional centrifugal impeller and FIG. 2 is a side sectional view. A conventional centrifugal impeller is composed of an abacus plate 1, a side plate 2, a collet 3 and a rotary shaft 4, The fluid is sucked into the suction port S1 and discharged to the impeller outlet S2 through the pulley passage formed of the main plate 1 and the side plate 2 and the collar 3 to apply energy to the fluid.

The impeller feathers 3 connect between the main plate and the side plates, and a plurality of impeller feathers are radially arranged and each impeller feather forms a slightly warped plate. The concave curved surface 3 'of the concave curved surface 3' and the curved convex surface 3 '' curved outwardly appear in the concave curved surface 3 ' 3 "). ≪ / RTI > Therefore, due to the peeling of the fluid flow on the concave surface 3 'of the impeller blade 3, the reverse flow region is generated as shown in FIG. 2 and the performance of the impeller is lowered.

Since the impeller has a limited number of vanes 3 and the fluid has a viscosity, the relative velocity at the impeller outlet 7 is changed differently from the exit vane angle due to friction in the vane passage, peeling of the flow, As the number of vanes 3 decreases, the discharge direction of the fluid gradually differs from the outlet angle.

Because of this phenomenon, the sliding velocity is generated at the impeller outlet (7) and the sliding velocity is generated in the direction opposite to the direction of rotation of the impeller, which causes the pressure head of the impeller to be decreased. The performance and efficiency of the impeller is reduced.

The performance deterioration of the centrifugal impeller is caused by the increase of the shaft force for driving the impeller and the deterioration of the efficiency. If some of these factors are removed, the performance of the centrifugal impeller is improved.

In the case of a centrifugal impeller having a small ratio of the outlet width to the diameter, since the difference between the radius of curvature of the side plate 4 and the curvature radius of the main plate 1 is small and the feather passage is long, the flow accelerated in the side plate inlet 2 ' Is accelerated again when reaching the impeller outlet (S2), and even if the static pressure is reduced at the side plate inlet (2 ') of the inlet, the flow in the vane passage accelerates without generating an overall deceleration, The flow is not peeled off at the side plate inlet 2 ', despite the pressure gradient in the largely formed catheter passage.

In the case of the centrifugal impeller having a large ratio of the outlet width to the diameter, since the difference between the radius of curvature of the side plate 2 and the radius of curvature of the main plate 1 is large and the feather passage is short, the flow accelerated at the side plate inlet 2 ' The speed distribution at the impeller outlet S2 is discharged in a state in which the side plate inlet 2 'is greatly increased as compared with the side of the main plate inlet 8 side.

At this time, according to the inner wall surface of the side plate 2, a flow phenomenon similar to the flow phenomenon occurs in which a back pressure gradient with strong flow is formed, so strong peeling phenomenon occurs at the side plate inlet 2 ' The jet path of the inner wall surface of the side plate 2 is completely shut off, and a strong backwash region is formed at the side plate outlet 2 ".

When such a phenomenon occurs, due to the peeled flow, the feather passage of the inner wall surface of the side plate 2 is completely shut off, so that the radial velocity is greatly reduced at the side plate outlet 2 ", and the sliding velocity is rapidly increased, The performance and the efficiency of the impeller are significantly deteriorated.

However, as the width of the impeller feather passage increases, the flow is peeled off from the side plate as shown in Fig. 2, causing a swirling flow in the impeller feather passage, resulting in energy loss due to peeling.

When a conventional centrifugal impeller is applied to a flow-through type blower, the flow from the impeller discharge port is radially discharged and vertically enters the wall of the duct (D) as shown in FIG. 2, The energy is dissipated due to the collision at the wall of the duct (D), and the loss is increased, so that the efficiency of the flow-through type blower is reduced.

In addition, the sliding speed is a factor that greatly affects the performance of the centrifugal impeller. As the sliding speed increases, the efficiency of the centrifugal impeller is greatly reduced.

In this way, the formation of the countercurrent region, that is, the part of the vane passage due to the separation of the flow, is blocked, and the radial velocity and the tangential velocity in the countercurrent region are reduced, thereby deteriorating the performance of the impeller.

Korean Patent Publication No. 10-2005-0074360 Korean Utility Model Registration No. 20-0241247

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems,

The swash plate of the abacus is formed obliquely at an angle of inclination ([theta]), and the vanes are formed on the inclined swash plate, so that the flow is smoothly transferred because no fluid is generated between the vanes and the vanes during rotation of the impeller The present invention aims to provide a structure of a hollow blade cross-section impeller impeller in which the direction of discharge from an impeller discharge port is changed from a radial direction to an axial direction so that the flow energy is efficiently utilized and the operating efficiency of the impeller is increased to greatly improve the performance of the blower have.

Further, by forming a hollow space portion inside the end surface of the impeller, it is possible to use it in an axial flow type humidifier. In application, the flow in the impeller is smoothly flowed to change the discharge direction naturally in the axial direction, Thereby improving the efficiency of the axial flow type blower, changing the operating point, improving the flow in the impeller pulley passage, reducing the noise generated in the impeller, and eliminating the risk of structural damage to the rotating shaft when the impeller is started Another object of the present invention is to provide a structure of a hollow wing cross-section impeller impeller which reduces the weight moment of the impeller by reducing the weight of the impeller by forming a steel plate so as to reduce the weight of the impeller.

In order to accomplish the above object, the present invention provides a rotary compressor comprising: a rotary shaft to which a rotary force is transmitted;

A main plate on which the rotating shaft is fixedly installed at a central portion and is rotated by a rotating shaft, an outer peripheral edge of which is inclined at an acute angle? With respect to a reference point C so that fluid is smoothly transferred;

A hollow wing cross-sectional collet attached to one end face of the swash plate of the main plate and having a hollow space formed therein so as to transfer the fluid to one side when the main plate rotates;

And a side plate formed on an upper surface of the hollow wing cross-sectional member and having a suction port formed therein to allow fluid to flow into the central portion thereof.

As described above, in the structure of the hollow blade section impeller blend impeller according to the present invention, the swash plate of the abacus plate is formed obliquely at a stagger angle ([theta]) and the swash plate is formed on the inclined swash plate, The flow is smoothly transferred without generating peeling (vortex) between the vanes and the vanes, and the direction of discharge from the impeller discharge port is changed from the radial direction to the axial direction so that the flow energy is efficiently utilized and the operating efficiency of the impeller is increased, The performance of the present invention is significantly improved.

Further, by forming a hollow space portion inside the end surface of the impeller, it is possible to use it in an axial flow type humidifier. In application, the flow in the impeller is smoothly flowed to change the discharge direction naturally in the axial direction, Thereby improving the efficiency of the axial flow type blower, changing the operating point, improving the flow in the impeller pulley passage, reducing the noise generated in the impeller, and eliminating the risk of structural damage to the rotating shaft when the impeller is started The weight of the impeller is reduced by forming a steel plate so that the inside diameter of the blade section is reduced to reduce the moment of inertia of the impeller.

1 is a front view of a conventional centrifugal impeller,
2 is a side view of a conventional centrifugal impeller,
FIG. 3 is a plan view of a hollow wing cross-sectional edge-type mixed impeller according to an embodiment of the present invention,
4 is a side cross-sectional view of a hollow wing cross-section veneer impeller according to an embodiment of the present invention,
FIG. 5 is a graph showing the relationship between the number of flow meters and the number of pressure meters of a fan according to an embodiment of the present invention,
FIG. 6 is a graph showing the total efficiency of the fans according to the variation of the dummy plow according to an embodiment of the present invention,
FIG. 7 is a graph showing changes in the maximum total efficiency of the fan, the change of the flow meter, and the change of the specific speed according to the change in the damping angle according to the embodiment of the present invention,
8 is a graph showing the relationship between air volume and voltage according to an embodiment of the present invention,
9 is a graph showing the relationship between air volume and voltage efficiency according to an embodiment of the present invention.

The present invention has the following features in order to achieve the above object.

The present invention relates to a rotary shaft,

A main plate on which the rotating shaft is fixedly installed at a central portion and is rotated by a rotating shaft, an outer peripheral edge of which is inclined at an acute angle? With respect to a reference point C so that fluid is smoothly transferred;

A hollow wing cross-sectional collet attached to one end face of the swash plate of the main plate and having a hollow space formed therein so as to transfer the fluid to one side when the main plate rotates;

And a side plate formed on an upper surface of the hollow blade crosspiece and having a suction port for allowing a fluid to flow in a central portion thereof.

The present invention having such characteristics can be more clearly described by the preferred embodiments thereof.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Before describing in detail several embodiments of the present invention with reference to the accompanying drawings, it is to be understood that the present invention is not limited to the details of construction and the arrangement of components shown in the following detailed description or illustrated in the drawings will be. The invention may be embodied and carried out in other embodiments and carried out in various ways. It should also be noted that the device or element orientation (e.g., "front," "back," "up," "down," "top," "bottom, Expressions and predicates used herein for terms such as "left," " right, "" lateral," and the like are used merely to simplify the description of the present invention, Or that the element has to have a particular orientation. Also, terms such as " first "and" second "are used herein for the purpose of the description and the appended claims, and are not intended to indicate or imply their relative importance or purpose.

Therefore, the embodiments described in this specification and the configurations shown in the drawings are merely the most preferred embodiments of the present invention and do not represent all the technical ideas of the present invention. Therefore, It is to be understood that equivalents and modifications are possible.

FIG. 3 is a plan view of a hollow wing cross-sectional winged type mixed impeller according to an embodiment of the present invention, FIG. 4 is a side sectional view showing a hollow wing cross-sectional wing mixed impeller according to an embodiment of the present invention, FIG. 6 is a graph showing the relationship between the number of flowmeters and the pressure coefficient of a fan according to an embodiment of the present invention. FIG. FIG. 7 is a graph showing a change in the maximum total efficiency of the fan, a change in the flow rate, and a change in the specific velocity according to a change in the duetriding angle according to an embodiment of the present invention. FIG. 9 is a graph showing the relationship between air volume and voltage efficiency according to an embodiment of the present invention. FIG.

3 to 9, the hollow blade section impeller blend impeller structure of the present invention comprises a rotating shaft 10, a main plate 20, a vane 30, and a side plate 40.

3 to 4, the rotary shaft 10 is fixed to a central portion of the main plate 20 and the other side is disposed inside the duct D to transmit a rotational force. 10 is protruded from the inside of the duct D to the outside and connected to a rotating device (not shown) such as a motor and is rotated by the rotating device to transmit rotational force to the main plate 20. [

3 to 4, the main plate 20 is formed as a circular plate, and a rotary shaft 10 is fixed to the center of the lower end surface. The main plate 20 is rotated by the rotary shaft 10 The swash plate 21 is formed so that the outer circumference of the main plate 20 is inclined at a sweep back angle? Relative to the reference point C.

4, the swash plate 21 is formed in the shape of "∧" on the basis of the reference point C at the both ends of the outer peripheral edge of the horizontally formed main plate 20, so that the flow of the fluid is smoothly transferred . At this time, the inclined plate 21 of the swash plate 21 is formed at an angle of 10 to 45 degrees with respect to the horizontal line of the abacus plate 20 so that the flow of the fluid is smoothly transferred. When the abacus plate 20 rotates, The swirling phenomenon does not occur between the vanes 30 and the fluid introduced through the suction port 41 of the impeller 40 is changed from the radial direction to the axial direction.

As shown in FIG. 5, the relationship between the flow coefficient and the pressure coefficient according to the durometer angle θ of the swash plate 21 is as follows. As shown in FIG. 5, And 0.34 for θ = 17.5 °, 0.49 for θ = 35 °, and 0.55 for θ = 52.5 °, respectively.

In the case of the total efficiency of the fan shown in Fig. 6, it is 52% at 0.20 for θ = 17.5 degrees, 49% at 0.29 for θ = 35 degrees, and 52.5 degrees at θ = The maximum total efficiency was 0.31 to 38%. In other words, it can be seen that there is a large change in the maximum flow rate and the position of the maximum total efficiency shifts toward a larger flow rate as the dummy angle (θ) of the impeller abacus increases.

As shown in FIG. 7 (a), the maximum total efficiency increases sharply in the range from 0 to 17.5 degrees, and the maximum total efficiency is increased to 17.5 The maximum total efficiency decreased gradually in the range of θ = 35 degrees and the maximum total efficiency decreased sharply after θ = 35 degrees.

As shown in FIG. 7 (b), the flow coefficient increases from θ = 0 ° to θ = 35 °, and θ = 35 ° after the maximum total efficiency according to the after- The tendency of increasing the number of flowmeters is remarkably reduced. As shown in FIG. 7 (c), it is found that the specific velocity increases with an increase in the damping angle, and the variation of the specific velocity from θ = 17.5 degrees to It can be seen that the specific speed is rapidly increased.

As described above, it is necessary to form the angle of inclination? Of the swash plate 21 at an angle of 10 to 45 degrees so that the flow meter and the pressure meter are stable and the total efficiency is good.

3 to 4, the vane 30 is attached to one end surface of the swash plate 21 of the main plate 20, that is, to the upper surface of the swash plate 21 as shown in FIG. 4, The pulsator 30 is also rotated at the same time as the pulley 30 rotates by the pulley 10 so as to allow the fluid to flow through the suction port 41 of the side plate 40 and to transfer the introduced fluid to one side .

Referring to FIG. 3, a plurality of the vanes 30 are formed radially on the basis of a central portion of the main plate 20, with the vanes 30 protruding perpendicularly from one end surface of the swash plate 21, A side plate 40 is attached to the upper surface of the plurality of vanes 30 to form a fluid passage 31 between the vanes 30 and the vanes 30 so that the fluid transferred through the fluid passage 31 is discharged. A discharge port 32 is formed at one side of the fluid channel 31.

As shown in FIG. 3, the vanes 30 are formed as a wing section, and are formed as hollow vane section vanes 30 having a hollow space 33 therein. The vanes 30, An impeller is used in various types of blowers such as an axial flow type flow fan and a flow rate blower.

As shown in FIGS. 3 to 4, the side plate 40 is formed as a circular plate having a suction port 41 to allow fluid to flow in the central portion thereof. The suction port 41 is formed in a generally donut- And is provided on the upper surface of the collar 30 to serve as a partition so as to form a fluid passage 31 between the collar 30 and the collar 30.

Referring to FIG. 4, the side plate 40 is provided on the upper surface of the collar 30. The side plate 40 is spaced apart from the upper surface of the swash plate 21 by a predetermined distance. The side plate 40 is also formed to be inclined in the shape of "? &Quot; At this time, the inclination angle of the side plate 40 may be the same as or different from that of the inclined plate 21 according to the vertical width of the vowel 30. Accordingly, the discharge port 32 of the fluid channel 31 is formed in various sizes.

The suction port 41 of the side plate 40 is formed to be inclined so that the suction port 41 of the side plate 40 is formed larger than the diameter of the suction port S1 of the conventional side plate 2 shown in FIG.

As described above, the hollow wing cross-sectional jet impeller 50 described above is formed so that the fluid flows in the axial direction in the radial direction, and is applied to a generally used axial flow type blower and a flow-through type blower.

4, the flow discharged from the outlet of the impeller is substantially parallel to the duct (D), and the energy dissipation from the wall of the tube The efficiency of the flow-through type blower is increased as shown in Figs. 8 and 9.

In addition, in the hollow blade cross-section impeller 50, the inclined plate 21 is deformed obliquely to form a mixed impeller 50 such that the shape of the general centrifugal impeller flows in the axial direction in the radial direction of the fluid.

10: rotating shaft 20: abacus
21: swash plate 30: hollow wing cross-section collar
31: Fluid flow path 32:
33: space part 40: side plate
41: inlet port 50: mixed impeller

Claims (5)

A rotating shaft 10 to which rotational force is transmitted;
The swash plate 21 is formed so that the swash plate 21 is fixed at the center and rotated by the rotating shaft 10 and the outer circumference of the swash plate 10 is obliquely inclined with respect to the reference point C, An abacus plate (20);
A hollow blade cross section 30 attached to one end surface of the swash plate of the main plate 20 and having a hollow space 33 formed therein for transferring the fluid to one side when the main plate 20 is rotated;
A side plate (40) formed on an upper surface of the hollow blade cross section (30) and having a suction port (41) for allowing fluid to flow in the center part; ≪ / RTI >
Wherein the hollow blade cross section (30) has a space (33) formed therein so as to be hollow, thereby reducing the weight of the impeller, thereby reducing the moment of inertia of the impeller. Structure.
The method according to claim 1,
The hollow wing cross-sectional feathers 30 are formed in such a manner that the hollow wing cross-sectional feathers 30 protrude perpendicularly from one end face of the swash plate 21 and are radially formed with respect to the center of the main plate 20, A side plate 40 is attached to an upper surface of the hollow wing cross-sectional member 30 so that a fluid channel 31 is formed between the hollow wing cross-sectional member 30 and the hollow wing cross-sectional member 30. The fluid conveyed through the fluid channel 31 And a discharge port (32) is formed at one side of the fluid flow path (31) so as to discharge the fluid.
3. The method of claim 2,
The inclined angle θ of the swash plate 21 is set such that the fluid introduced through the suction port 41 of the side plate 40 and the fluid fed by the hollow blade cross- Is formed at an angle of 10 to 45 degrees so as not to be peeled off from the flow path (31), so that the fluid is smoothly conveyed.
The method according to claim 1,
Wherein the side plate (40) is formed as a circular plate having a suction port (41) at a central portion thereof, and a circumferential surface thereof is formed to be inclined in accordance with a tail angle (?) Of the swash plate.
3. The method of claim 2,
Wherein the mixed impeller 50 is installed in the duct D so that the fluid discharged through the discharge port 32 of the fluid passage 31 is conveyed in the axial direction on the duct D. [ Structure of mixed impeller.

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