KR20100112307A - Fluid stabilizer for axial-flow impeller - Google Patents

Abstract

PURPOSE: A fluid stabilizer for an axial-flow impeller is provided to prevent stall and the backflow of fluid and thereby improve the performance and efficiency of a system using an axial-flow impeller. CONSTITUTION: A fluid stabilizer for an axial-flow impeller comprises an adjustment hole(31), an adjustment rib(32), a sensor part, and a driving part(33). The adjustment hole is formed in a case(10) to face the tip of blades according to the rotation of a rotary shaft. The adjustment rib is fitted to seal the adjustment hole. The sensor unit generates a driving signal according to a precursor signal of stall created between the tip of the blades and the case. The driving part slides the adjustment rib within the adjustment hole according to the driving signal of the sensor part, thereby forming an uneven portion on the interior surface of the case.

Description

Fluid stabilizer for axial-flow impeller

The present invention relates to a fluid stabilization device for an axial flow impeller, and more specifically, through the adjustment hole formed in the case facing the wing tip of the axial impeller, and close the control hole by inserting the adjustment rib in close contact with the adjustment hole, By moving the adjusting rib in accordance with a separate driving signal to form irregularities on the surface of the case, it is possible to suppress or prevent instability (stall generation, etc.) occurring below the critical point due to the rotation of the axial impeller. The present invention relates to a fluid stabilization device for an axial impeller that can improve the performance and efficiency of an axial impeller.

1 is a side view illustrating an axial flow impeller according to the prior art. Referring to FIG. 1, the axial flow impeller 200 is rotated about a rotation axis 210, and a plurality of wings along an edge of the rotation axis 210. 220 is fixed. Here, the boss 230 may be installed on the rotation shaft 210 to facilitate fixing of the blade 220. The axial impeller 200 is installed inside the case 100 to transfer the fluid on the suction side to the discharge side. Here, the blade 220 may be spaced apart along the longitudinal direction of the rotating shaft 210, the vane 220 is spaced between the wing 220 and the blade 220 is installed in the space between the vane 110 can be increased static pressure have. Here, a small space is formed between the tip of the blade 220 of the axial impeller 200 and the case 100.

However, the axial impeller according to the prior art has a problem that stall occurs when a critical point is passed due to an unexpected situation during operation in a section of low flow rate and high pressure having high efficiency among performance curves.

In addition, there is a problem that the pressure ratio is lowered due to the generation of stall, the efficiency is lowered, and the blades cause severe vibration.

In addition, there is a problem that a surge occurs due to the generation of a stall, causing fluid to flow back, or to cause unstable behavior in a system in which an axial impeller is used.

For example, in the case of an axial compressor using an axial impeller, when the axial compressor is connected to the combustor and the turbine, there is a problem that the temperature of the fluid entering the combustor is increased and the temperature entering the turbine is overheated.

Accordingly, an object of the present invention is to solve such a conventional problem, a stall that occurs when a critical point is passed due to an unexpected situation during operation in a low flow rate and high pressure section having high efficiency among the performance curves of an axial impeller ( It is to provide a fluid stabilization device of the axial impeller that can suppress or prevent the stall.

In addition, the present invention provides a fluid stabilization device for an axial impeller that can prevent a pressure ratio from falling and prevent the blade from vibrating.

In addition, the present invention provides a fluid stabilization device for an axial impeller that can improve the performance and efficiency of the system in which the axial impeller is used.

The present invention also provides a fluid stabilization device for an axial flow impeller that prevents backflow of fluid and can stabilize the behavior of a system in which an axial flow impeller is used.

According to the present invention, in the fluid stabilization device of the axial impeller in which the blade is disposed along the circumferential direction of the rotating shaft to rotate inside the case, in the case facing the end of the blade in accordance with the rotation of the rotating shaft Control holes formed; An adjustment rib inserted in close contact with the control hole; A sensor unit generating a driving signal according to a precursor signal for a stall generated between the case and the tip of the blade; A driving unit for slidingly moving the adjusting rib in the adjusting hole according to the driving signal of the sensor unit; It comprises, and is achieved by the fluid stabilization device of the axial flow impeller, characterized in that to form an unevenness on the inner surface of the case as the adjusting rib is moved.

Wherein the sensor unit is driven by comparing the flow rate measuring unit for measuring the flow rate of the fluid flowing into the case, the flow rate measured by the flow rate measuring unit and the reference flow rate set according to the axial flow impeller so that no stall occurs It is preferable to include a flow rate signal portion for generating a signal.

The sensor unit may include a pressure measuring unit measuring at least one of a pressure on the suction side and a pressure on the discharge side of the case, and a pressure and a stall measured at the pressure measuring unit so that the pressure and the stall do not occur. It is preferable to include a pressure signal unit for generating a drive signal by comparing the reference pressure set according to.

The sensor unit may further include a calculation unit configured to calculate a pressure ratio between the suction side and the discharge side based on the pressure on the suction side and the discharge side measured by the pressure measuring unit, and the pressure signal unit is calculated by the calculation unit. It is preferable to generate a drive signal by comparing the pressure ratio set in accordance with the axial impeller so as to prevent the generated pressure ratio and the stall.

Here, a rib coupling portion for integrating the adjustment ribs formed in each divided section by dividing at least two portions along the outer circumferential surface of the case is further formed, and the driving portion is coupled to the rib coupling portion to slide the adjustment rib. desirable.

According to the present invention, the fluid stabilization of the axial impeller that can suppress or prevent the stall (stall) generated after the critical point due to an unexpected situation during operation in the low flow rate, high pressure section having a high efficiency of the axial impeller performance curve An apparatus is provided.

Further, there is provided a fluid stabilization device for an axial impeller that can prevent the pressure ratio from falling and prevent the blades from vibrating.

In addition, there is provided a fluid stabilization device for an axial impeller that can improve the performance and efficiency of a system in which an axial impeller is used.

In addition, there is provided a fluid stabilization device for an axial impeller that prevents backflow of fluid and can stabilize the behavior of a system in which an axial impeller is used.

In addition, there is provided a fluid stabilization device for the axial impeller that can improve the stability of the axial impeller, and to expand or improve the operating range.

In addition, there is provided a fluid stabilization device of the axial impeller that can detect the occurrence of stall before the stall (stall) occurs, and can adjust the shape and depth of the irregularities formed on the inner surface of the case.

Prior to the description, in the various embodiments, components having the same configuration will be representatively described in the first embodiment using the same reference numerals, and in other embodiments, different configurations from the first embodiment will be described. do.

Hereinafter, with reference to the accompanying drawings will be described in detail with respect to the fluid stabilizer of the axial flow impeller according to an embodiment of the present invention.

The axial impeller of the present invention is used in an axial blower or an axial compressor or an axial pump or a gas turbine engine. In an embodiment of the present invention, an axial impeller used in an axial compressor will be described as an example.

2 is a side view showing an axial flow impeller according to an embodiment of the present invention, Figure 3 is a plan view schematically showing the structure of the case in the axial flow impeller according to an embodiment of the present invention.

2 and 3, the axial flow impeller 20 according to an embodiment of the present invention is rotated about the rotation shaft 21, and a plurality of wings 22 are disposed and fixed along the edge of the rotation shaft 21. do. Here, the boss 23 may be installed on the rotation shaft 21 to facilitate the fixing of the vanes 22. The axial impeller 20 is installed inside the case 10 to transfer the fluid on the suction side to the discharge side. Here, the blades 22 may be spaced apart along the longitudinal direction of the rotation shaft 21, and the vane 11 may be installed in the space between the blades 22 and the blades 22 spaced apart to increase the static pressure. have. Here, a small space is formed between the tip of the blade 22 and the case 10 of the axial impeller 20.

When the inner surface of the case 10 is flat, the stall is formed by the interaction between the vortex and the inlet flow generated as the fluid passes from the tip of the blade 22 to the discharge side due to the rotation of the axial impeller 20. Occurs. At this time, by providing the fluid stabilization device 30 in the case 10 facing the end of the blade 22, it is possible to suppress or prevent the generation of a stall (stall).

In an embodiment of the present invention, the fluid stabilization device 30 may be divided into an adjustment hole 31, an adjustment rib 32, a sensor unit (not shown), and a driving unit 33.

The adjusting hole 31 is formed through the case 10 facing the end of the blade 22 as the rotating shaft 21 of the axial impeller 20 rotates. The arrangement interval and shape of the adjustment hole 31 formed in the case 10 can be changed according to the specifications of the axial impeller 20. In one embodiment of the present invention, the shape of the adjustment hole 31 is shown as an embodiment through FIG. 4, but not limited to the arrangement interval and shape of the adjustment hole 31 in the present invention, although not shown, several types It may be polygonal or circular, and may be formed in a zigzag or wavy shape. The present invention is sufficient to form the adjusting hole 31, it is within the scope of the present invention to change the arrangement interval and shape of the adjusting hole (31).

4 is a development view schematically showing the shape of the adjustment hole formed in the case in the axial impeller according to an embodiment of the present invention, the rotation of the rotary shaft 21 at the portion facing the end of the wing 22 It is a figure which shows the case 10 extended along the direction.

Referring to FIG. 4, the case 10 has an adjustment hole 31 formed in a direction perpendicular to the direction of rotation of the rotation shaft 21 as shown in (a), and the adjustment hole 31 is the rotation shaft 21. Can be spaced apart along the direction of rotation of the.

In addition, in the case 10, as shown in (b), the adjustment hole 31 is formed to be inclined to one side in the rotation direction of the rotation shaft 21, and the adjustment hole 31 is along the rotation direction of the rotation shaft 21. Can be spaced apart. The adjustment hole 31 shown in (b) is inclined to one side the adjustment hole 31 shown in (a).

In addition, as shown in (c), the case 10 has an adjustment hole 31 formed in parallel with the rotation direction of the rotation shaft 21, and the adjustment hole 31 is perpendicular to the rotation direction of the rotation shaft 21. It may be spaced apart along the direction. Adjusting hole 31 shown in (c) is preferably formed at least two divided along the outer peripheral surface of the case (10).

The adjusting rib 32 is tightly inserted to close the adjusting hole 31 described above. The adjusting rib 32 may preferably seal the adjusting hole 31 such that the fluid flowing in the case 10 does not flow out through the adjusting hole 31. In addition, the adjustment rib 32 is inserted into the adjustment hole 31 so that the inner surface of the case 10 is formed in a flat shape without the unevenness, the adjustment hole 31 in accordance with the operation of the drive unit 33 to be described later. The slide is moved so that the uneven surface is formed on the inner surface of the case (10).

The adjusting rib 32 thus formed may be integrally formed by the rib coupling part 34. The rib coupling part 34 is formed in each divided section divided into at least two parts along the outer circumferential surface of the case 10, and integrates the adjusting ribs 32 formed in the divided sections. Then, in each divided section, the adjusting ribs 32 are formed to protrude from the rib coupling part 34, respectively, and the adjusting ribs 32 are formed to be inserted into the adjusting holes 31. The rib coupling portion 34 is divided by dividing the outer circumferential surface of the case 10 along the rotation direction of the rotation shaft 21, like the rib coupling portion 34 formed on the axial impeller 20 shown in FIG. 2. It is formed in the section, it can be divided again in the longitudinal direction of the rotary shaft 21 according to the blades 22 are spaced apart in the longitudinal direction of the rotary shaft (21).

In addition, the rib coupling portion 34, like the rib coupling portion 34 formed in the lower portion of the axial impeller 20 shown in Figure 2 by dividing the outer peripheral surface of the case 10 along the rotational direction of the rotary shaft 21 It is formed in the divided section, it is possible to integrate the rib coupling portion 34 in the longitudinal direction of the rotary shaft 21 in accordance with the blades 22 are spaced apart in the longitudinal direction of the rotary shaft (21). Then, the adjustment ribs 32 coupled to the rib coupling units 34 can be simultaneously operated for each divided section along the rotational direction of the rotary shaft 21, and the control of the driving unit 33 to be described later can be simplified. have.

Although not shown, the sensor unit (not shown) generates a driving signal according to a precursor signal for a stall generated between the case 10 and the tip of the blade 22.

Here, the precursor signal is a signal that previously detects the generation of a stall near the threshold of the stall before the stall occurs in a flat state where the inner surface of the case 10 has no unevenness. This is a small amount of disturbance that occurs before). These precursor signals are experimental data values that can be determined according to the specifications of the axial impeller 20, and the precursor signals are preset according to the specifications of the axial impeller 20. Then, the sensor unit (not shown) generates a driving signal according to the precursor signal.

First, the sensor unit (not shown) may be configured to include a flow measurement unit (not shown) and a flow signal unit (not shown). The flow rate measuring unit (not shown) measures the flow rate of the fluid flowing into the case 10, and the flow rate signal unit (not shown) measures the flow rate and the reference flow rate (F1, FIG.) Measured by the flow rate measuring unit (not shown). 6) to generate a drive signal. Reference flow rate F1 (refer FIG. 6) is the flow volume set with the axial impeller 20 so that stall may not generate | occur | produce, It is determined according to the specification of the axial impeller 20 by the above-mentioned precursor signal.

Second, the sensor unit (not shown) may be configured to include a pressure measuring unit (not shown) and a pressure signal unit (not shown). The pressure measuring unit (not shown) may measure at least one of the pressure at the suction side and the pressure at the discharge side of the case 10. The pressure signal unit (not shown) generates a driving signal by comparing the pressure on the suction side or the pressure on the discharge side with the reference pressure measured by the pressure measuring unit (not shown). Here, the reference pressure is a pressure on the suction side or a discharge side set by the axial impeller 20 so that a stall does not occur, and is determined according to the specifications of the axial impeller 20 by the above-described precursor signal. .

The sensor unit (not shown) may further include a calculation unit (not shown). The calculator (not shown) calculates the pressure ratio using the pressure on the suction side and the pressure on the discharge side measured by the pressure measuring unit (not shown). In this case, the pressure signal unit (not shown) generates a driving signal by comparing the pressure ratio calculated by the calculator (not shown) with the reference pressure ratio PR1 (see FIG. 6). Here, the reference pressure ratio PR1 (refer to FIG. 6) is a pressure ratio set according to the axial impeller 20 so that no stall occurs. The reference pressure ratio PR1 is determined according to the specification of the axial impeller 20 according to the precursor signal described above. .

The driving unit 33 slides the adjusting rib 32 which is tightly inserted into the adjusting hole 31. In particular, the driving unit 33 is characterized in that it is operated by the drive signal of the above-described sensor unit (not shown). The driving part 33 is installed in the rib coupling part 34 to slide the plurality of adjustment ribs 32 at the same time. The driving unit 33 may be configured as a stepping motor or a cylinder, and the adjusting rib 32 may be configured to reciprocate in the adjusting hole 31. As the adjustment rib 32 slides in the adjustment hole 31 according to the operation of the driving unit 33, irregularities may be formed on the inner surface of the case 10.

The operation of one embodiment of the fluid stabilization device of the axial impeller described above will now be described.

Fluid stabilization device 30 according to an embodiment of the present invention is to prevent or prevent the stall (stall) by forming irregularities on the inner surface of the case 10 before the stall (stall), the axial flow impeller 20 ), The inner surface of the case 10 is flattened by removing the irregularities formed on the inner surface of the case 10.

5 is a plan view schematically illustrating a state in which a fluid stabilization device of an axial impeller is operated according to an embodiment of the present invention, and FIG. 6 is a relation between a flow rate and a pressure ratio in an axial flow impeller according to an embodiment of the present invention. Is a graph schematically.

In FIG. 6, the x axis represents a flow rate and the y axis represents a pressure ratio. The graph in which the pressure ratio decreases as the flow rate decreases based on the flow rate F1 among the graphs shown in FIG. 6 is a graph showing a relationship between the flow rate and the pressure ratio in a state in which the inner surface of the case 10 has no unevenness. 6, a graph in which the pressure ratio increases as the flow rate decreases based on the flow rate F1 in the graph shown in FIG. 6 is provided with irregularities on the inner surface of the case 10 before the stall is generated as in the embodiment of the present invention. When the axial impeller 20 is stabilized, the graph shows the relationship between the flow rate and the pressure ratio through the process of eliminating the unevenness formed on the inner surface of the case 10. According to one embodiment of the present invention, when the axial impeller 20 is operated as shown in FIG. 6, the pressure ratio increases as the flow rate decreases based on the flow rate F1.

Referring to the graph shown in FIG. 6, the pressure ratio according to the prior art and the pressure ratio according to the embodiment of the present invention change the same or similar to the flow rate change between F1 and F3, but according to the prior art, between F2 and F1. When the flow rate becomes smaller than F1 due to the change in the flow rate, the pressure ratio drops sharply, but according to one embodiment of the present invention, the pressure ratio may be increased from PR1 to PR2 for the flow rate change between F2 and F1. At this time, in one embodiment of the present invention, as the flow rate decreases based on the flow rate F1, the axial impeller 20 may be operated with a pressure ratio equal to or similar to that of the PR1. In other words, according to the present invention, even if the flow rate becomes smaller than F1 with respect to the flow rate change, it is sufficient if the pressure ratio can be suppressed or prevented from dropping rapidly as in the prior art.

In this case, when the flow rate is smaller than F1 in the state where the inner surface of the case 10 is absent, it can be predicted that a stall occurs because the pressure ratio drops rapidly, and thus the efficiency of the axial impeller 20 is lowered. . At this time, the flow rate F1 becomes a reference flow rate set by the precursor signal generated by the axial impeller 20. The flow rate F3 represents the flow rate maximum flowing into the case 10 when the axial impeller 20 operates.

When the pressure ratio is greater than PR1 in the state where the inner surface of the case 10 has no unevenness, since the pressure ratio drops rapidly, it is possible to predict that a stall is generated, thereby lowering the efficiency of the axial impeller 20. At this time, the pressure ratio PR1 becomes the reference pressure ratio set by the precursor signal generated by the axial impeller 20.

Although not shown, when there is no unevenness on the inner surface of the case 10, when the pressure on the suction side or the pressure on the discharge side becomes higher than a predetermined level, the pressure drops rapidly, so that a stall may be expected. As a result, the efficiency is lowered. At this time, the pressure on the suction side or the discharge side becomes a reference pressure set by the precursor signal generated by the axial impeller 20. When the axial impeller is compressing and the pressure ratio calculated by the calculation unit (not shown) is the discharge side pressure with respect to the suction side pressure of the case 10, the minimum pressure ratio will not be shown in the graph, but will be greater than one.

First, the operation of the axial impeller 20 in which a sensor unit (not shown) includes a flow rate measuring unit (not shown) and a flow rate signal unit (not shown) will be described with reference to FIGS. 5 and 6.

The inner surface of the first case 10 is an axial impeller 20 is operated by the rotation of the rotary shaft 21 in a flat state without the unevenness. At this time, the flow rate flowing into the case 10 through the flow measurement unit (not shown) is measured. And the flow rate measured by the flow rate measuring unit (not shown) through the flow signal unit (not shown) and compares the reference flow rate (F1). When the flow rate measured by the flow rate measuring unit (not shown) gradually decreases to be less than or equal to the above-described reference flow rate F1, the flow rate signal unit (not shown) generates a drive signal. The driving signal generated by the flow rate signal part (not shown) operates the driving part 33 to form irregularities on the inner surface of the case 10 as shown in FIG. 5. Then, even if the flow rate decreases to F2 due to the unevenness formed on the inner surface of the case 10, no stall occurs. Therefore, even if the flow rate further decreases by the value of F1-F2, stall does not occur in the axial impeller 20, and stable operation can be maintained.

In addition, when the flow rate measured by the flow measuring unit (not shown) exceeds the reference flow rate F1 in the state where the unevenness is formed on the inner surface of the case 10, a driving signal is generated through the flow signal unit (not shown). Let's do it. The driving signal generated by the flow rate signal part (not shown) operates the driving part 33 to remove the unevenness formed on the inner surface of the case 10 as shown in FIG. 3 to flatten the inner surface of the case 10. Return to. Therefore, in the flow rate variation section (section from F1 to F3) in which the axial impeller 20 can be operated without generating a stall according to the specification of the axial impeller 20, the inner surface of the case 10 is flat. It is to hold | maintain and to form an unevenness | corrugation centering around the reference flow volume F1, so that a stall may not generate | occur | produce even below the reference flow volume F1.

Second, the operation of the axial flow impeller 20 configured by the sensor unit (not shown) including a pressure measuring unit (not shown), a calculation unit (not shown) and a pressure signal unit (not shown) with reference to FIGS. It demonstrates.

The inner surface of the first case 10 is an axial impeller 20 is operated by the rotation of the rotary shaft 21 in a flat state without the unevenness. At this time, the pressure is measured on the suction side and the discharge side of the case 10 through a pressure measuring unit (not shown). And the pressure ratio is calculated through the calculation unit (not shown) by using the pressure measured in the pressure measuring unit (not shown). The pressure ratio calculated by the calculator (not shown) and the reference pressure ratio PR1 are compared through the pressure signal unit (not shown). When the pressure ratio calculated by the calculation unit (not shown) gradually increases to be equal to or greater than the above-described reference pressure ratio PR1, the pressure signal unit (not shown) generates a driving signal. The driving signal generated by the pressure signal part (not shown) operates the driving part 33 to form irregularities on the inner surface of the case 10 as shown in FIG. 5. Then, even if the pressure ratio increases to PR2 due to the unevenness formed on the inner surface of the case 10, no stall occurs. Therefore, even if the pressure ratio increases by the value of PR2-PR1, stall does not occur in the axial impeller 20, and stable operation can be maintained.

In addition, when the pressure ratio calculated by the calculation unit (not shown) becomes smaller than the reference pressure ratio PR1 while the unevenness is formed on the inner surface of the case 10, a driving signal is generated through the pressure signal unit (not shown). . The driving signal generated by the pressure signal unit (not shown) operates the driving unit 33 to remove the unevenness formed on the inner surface of the case 10 as shown in FIG. 3 to flatten the inner surface of the case 10. Return to. Therefore, the inner surface of the case 10 is flat in the pressure change section (section where the pressure ratio is smaller than PR1) in which the axial impeller 20 can be operated without generating a stall according to the specification of the axial impeller 20. It is to hold | maintain and to form an unevenness | corrugation centering on the reference pressure ratio PR1 so that a stall may not generate | occur | produce even more than reference pressure ratio PR1.

Third, the operation of generating the drive signal using the pressure on the suction side or the pressure on the discharge side generates the drive signal at or above the reference pressure.

The sensor unit (not shown) may include both a flow measuring unit (not shown), a flow signal unit (not shown), a pressure measuring unit (not shown), a calculating unit (not shown), and a pressure signal unit (not shown). Can be.

Figure 7 is a graph schematically showing the relationship between the flow rate and the efficiency in the axial flow impeller according to an embodiment of the present invention. In FIG. 7, the x axis represents the flow rate, and the y axis represents the efficiency. 7 shows the relationship between the efficiency and the flow rate calculated according to an embodiment of the present invention, the efficiency of the flow rate change between F1 and F3 is uneven on the inner surface of the case as in the prior art It is the same or similar to the calculated efficiency if it is not formed. 7 shows the relationship between the efficiency and the flow rate calculated when the unevenness is always formed on the inner surface of the case 10.

Referring to FIG. 7, the flow rate between F1 and F3 represents the efficiency exhibited according to the normal operation of the axial impeller 20, and the efficiency according to the embodiment of the present invention at the flow rate between F1 and F3 is the same as that of the related art. Or similar efficiency is shown, but when the unevenness is formed on the inner surface of the case 10 at the flow rate between F1 and F3, the efficiency is significantly reduced for the same flow rate. However, even if the flow rate decreases from the reference flow rate F1, although the unevenness is formed on the inner surface of the case 10, although the efficiencies of the axial flow impeller operate stably, although the efficiency is low, in the case of the prior art, the efficiency decreases and stalls. Stall occurrences result in unstable drive of the axial impeller.

According to an embodiment of the present invention, when the flow rate decreases from the reference flow rate F1, since the driving signal generated through the sensor unit (not shown) forms irregularities on the inner surface of the case 10, F1 and F3 In the flow rate between the axial flow impeller is operated at high efficiency as in the prior art, and when the flow rate decreases from the F1 becomes the reference flow rate, but decreases to a low efficiency as if the unevenness is formed on the inner surface of the case 10, It is to make the axial impeller operate stably.

The scope of the present invention is not limited to the above-described embodiment, but may be embodied in various forms of embodiments within the scope of the appended claims. Without departing from the gist of the invention claimed in the claims, it is intended that any person skilled in the art to which the present invention pertains falls within the scope of the claims described herein to various extents that can be modified.

1 is a side view showing an axial flow impeller according to the prior art,

Figure 2 is a side view showing an axial flow impeller according to an embodiment of the present invention,

Figure 3 is a plan view schematically showing the structure of the case in the axial impeller according to an embodiment of the present invention,

Figure 4 is a schematic exploded view showing the shape of the adjusting hole formed in the case in the axial impeller according to an embodiment of the present invention,

5 is a plan view schematically showing a state in which the fluid stabilization device of the axial impeller operating according to an embodiment of the present invention,

6 is a graph schematically showing a relationship between a flow rate and a pressure ratio in an axial flow impeller according to an embodiment of the present invention;

7 is a graph schematically showing a relationship between flow rate and efficiency in an axial impeller according to an embodiment of the present invention.

<Explanation of symbols for the main parts of the drawings>

10, 100: case 11, 110: stator 20, 200: axial flow impeller

21, 210: rotating shaft 22, 220: wing 23, 230: boss

30: fluid stabilization device 31: adjustment hole 32: adjustment rib

33: drive portion 34: rib coupling portion

F1: reference flow rate PR1: reference pressure ratio

Claims (5)

In the fluid stabilization device of the axial impeller, the blades are disposed along the circumferential direction of the rotating shaft rotating inside the case, Adjusting hole formed in the case facing the end of the wing according to the rotation of the rotary shaft; An adjustment rib inserted in close contact with the control hole; A sensor unit generating a driving signal according to a precursor signal for a stall generated between the case and the tip of the blade; A driving unit for slidingly moving the adjusting rib in the adjusting hole according to the driving signal of the sensor unit; Including, The fluid stabilizer of the axial flow impeller, characterized in that for forming the irregularities on the inner surface of the case as the adjustment rib is moved. The method of claim 1, The sensor unit compares the flow rate measuring unit for measuring the flow rate of the fluid flowing into the case, the flow rate measured by the flow rate measuring unit and the reference flow rate set by the axial flow impeller so as not to generate a stall signal Fluid stabilization device of the axial flow impeller including a flow rate signal generating portion. The method of claim 1, The sensor unit according to the axial flow impeller so that the pressure measuring unit for measuring at least one of the pressure on the suction side and the discharge side in the case and the pressure and stall measured in the pressure measuring unit does not occur The fluid stabilization device of the axial impeller comprising a pressure signal unit for generating a drive signal by comparing the set reference pressure. The method of claim 3, The sensor unit further includes a calculation unit for calculating the pressure ratio between the suction side and the discharge side based on the pressure on the suction side and the discharge side measured in the pressure measuring unit, And the pressure signal unit generates a driving signal by comparing the pressure ratio calculated by the calculator with a reference pressure ratio set according to the axial impeller so that a stall does not occur. The method according to any one of claims 1 to 4, A rib coupling portion is further formed along the outer circumferential surface of the case to integrate the adjustment ribs formed in each divided section, and the driving portion is coupled to the rib coupling portion to slide the adjustment rib. Fluid stabilizer for axial impeller.

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