JP4413525B2 - Cross-flow fan wheel - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a once-through fan impeller applied to a once-through fan.
[0002]
[Prior art]
As a conventional once-through fan wheel, the arrangement pitch of adjacent blades arranged at a predetermined interval around the axis of the rotary shaft is set to a different length, and the chord length L of each blade is different from each other. A configuration in which the sum (Pp + Ps) / l of the arrangement pitch Pp on the pressure surface side and the arrangement pitch Ps on the suction surface side is set to be constant at a predetermined value K is already known (for example, Patent Reference 1).
According to the conventional once-through blower impeller having such a configuration, the chord length of each blade is not limited to the back pressure surface side, and the arrangement pitch on the suction surface side is also considered, and the chord length and each blade are considered. Since the arrangement pitch ratio can be set so as to ensure an optimum value for the fan blade cascade, the fan efficiency can be improved.
[0003]
Further, as another conventional once-through fan impeller, a plurality of partition plates perpendicular to the rotation axis and a plurality of blades arranged between these partition plates are provided, and the arrangement of the blades is changed cyclically. The thing of the structure which has been already known is also known (for example, refer patent document 2).
[0004]
[Patent Document 1]
JP-A-10-299694 (page 3-4, FIG. 1)
[Patent Document 2]
Japanese Patent Laid-Open No. 9-19579 (page 2-5, FIG. 1)
[0005]
[Problems to be solved by the invention]
Since the conventional cross-flow fan wheel is configured as described above, the cross-flow fan equipped with the impeller is improved in blade element efficiency and noise accompanying rotation of the blade wheel (number of rotations × number of blades) In order to reduce the noise generated in the low frequency range that is an integral multiple of the number of rotations, the blade mounting pitch and blade shape are merely changed in the circumferential direction of the impeller. The width and direction were constant, and there was a problem that a significant improvement in the static pressure recovery rate due to an increase in the diffuser expansion rate could not be realized due to separation and backflow on the diffuser wall. In addition, if the diffuser expansion ratio is increased with a once-through fan used in an air conditioner, a backflow of warm air from the living space into the diffuser occurs during cooling operation, and dew adheres to the diffuser wall surface, causing dew splattering and dripping. There was a problem.
[0006]
The present invention has been made to solve the above-described problems, and an object thereof is to obtain a once-through blower impeller that reduces the blower power without impairing noise, headwind characteristics, or dew adhesion resistance. To do.
[0007]
[Means for Solving the Problems]
The once-through blower impeller according to the present invention includes a plurality of blades arranged around the axis of the rotation axis and parallel to the rotation axis, and the arrangement group of the blades is divided into a plurality of blocks on a cross section perpendicular to the rotation axis. And each block is composed of at least two blades, and the blade tangent angle β1 defined on the inner diameter side of the impeller or the blade tangent angle β2 defined on the outer diameter side of the impeller or Both tangent angles β1 and β2 are different tangent angles for each block, and the same tangent angle is used in the block .
[0008]
DETAILED DESCRIPTION OF THE INVENTION
An embodiment of the present invention will be described below.
Embodiment 1 FIG.
1 is a cross-sectional view showing a cross-flow fan wheel according to Embodiment 1 of the present invention, and FIG. 2 is a front view of FIG.
A cross-flow blower impeller (hereinafter simply referred to as an impeller) 1 shown in FIG. 1 includes a rotating shaft 2 and a plurality of partition plates 3 integrally coupled at right angles to the rotating shaft 2 at regular intervals (see FIG. 2). And a plurality of blades 4 arranged around the axis of the rotary shaft 2 at a predetermined interval and parallel to the rotary shaft 2 between the partition plates 3. In such an impeller 1, the arrangement group of the blades 4 is divided into two blocks A and B on a cross section perpendicular to the rotation shaft 2. In this way, the arrangement group of the blades 4 divided into the two blocks A and B has the same tangent angle of the blades 4 for each of the blocks A and B, and the air flow blowing angle for each of the blocks A and B is periodically changed. It is formed to change.
[0009]
That is, in Embodiment 1, when the tangent angle of all the blades 4 defined on the inner diameter side of the impeller 1 is β1, the tangent angle β1 is equal to the tangent angle β11 of the blade 4 of the block A and the block B The tangent angle β12 of the blade 4 is different from the block A and the block B, and the tangential angle of the blade 4 is made different between β11 and β12.
[0010]
Next, the operation will be described. 3 (A) and 3 (B) are operation explanatory views showing the direction of air flow when the impeller 1 is rotated. In FIG. 3, 7 is a blowout air passage of the once-through fan.
When the impeller 1 rotates, when the block B of the blade 4 group is positioned on the side of the blowout air passage 7 of the cross-flow fan (see FIG. 3A), the block A of the blade 4 group is connected to the blowout air passage 7. When positioned on the air flow side (see FIG. 3B), the flow between the blades (between the blades 4) is caused by the difference between the tangent angles β11 and β12 of the blades 4 of the block A and the block B. As it changes, the slip amount changes, and the air flow blowing direction changes. For example, when the block A is located on the side of the blowing air path 7, as shown by an arrow b in FIG. 3B, a blowing air flow is formed upward, and the block B is located on the side of the blowing air path 7. Sometimes, a blowout airflow is formed downward as indicated by an arrow a in FIG.
[0011]
According to the first embodiment described above, in the once-through fan impeller 1 having a plurality of blades 4 arranged around the rotation shaft 2 and parallel to the rotation shaft 2, the group of the blades 4 is arranged. Is divided into two blocks A and B on a cross section perpendicular to the rotary shaft 2, and the tangential angle β1 of the blade 4 defined on the inner diameter side of the impeller 1 is set to be the tangential angle of the blade 4 of the one block A. By differentiating between β11 and the tangential angle β12 of the blade 4 of the other block B, when the impeller 1 rotates, the airflow blowing angle is periodically between the one block A and the other block B. Since it is configured to change, the direction of the blown airflow can be periodically changed. The direction change of the blown airflow promotes turbulence in the boundary layer of the wall surface of the blowout air passage 7, and the main stream of the blown airflow is blown out. Peel from the wall of the air passage 7 It has the effect that it is possible to suppress the backflow of meaning peeling, and balloon airflow to. Furthermore, since the rotation speed of a general once-through fan impeller is several hundred to several thousand r / min, and the direction of the airflow changes in a high cycle, the effect is that a wide diffusive blown airflow is generated on average. There is.
[0012]
FIG. 4 is a diagram showing the ratio of the diffuser expansion ratio between the conventional impeller and the impeller of the present invention and the blowing power at the same air volume.
As is apparent from FIG. 4, according to the first embodiment, even if the enlargement ratio of the diffuser is increased due to the above-described physical phenomenon, the blown air flow is hardly separated and the reverse flow does not occur, the diffuser efficiency is improved, and the blowing power is increased. Is obtained.
[0013]
In the first embodiment, the case where the tangent angles β1 of all the blades 4 are two types of blocks A and B and the tangent angles of the blades 4 are β11 and β12 is described. The impeller 1 may be configured to have β1 of the same number as a plurality of blocks including at least two or more blades as one block. In this case, the same effect can be obtained. Furthermore, in the blade element (blade) shape of FIG. 1, the warp line is a single arc, the thickness is a uniform thickness distribution, and the blade tip shape is a semicircular arc, but the warp line, the thickness distribution, the blade tip shape, etc. Is not specified, and the same effect as in the first embodiment is obtained by the circumferential distribution of the tangent angle β1 of the blade 4.
[0014]
Embodiment 2. FIG.
FIG. 5 is a cross-sectional view showing a cross-flow fan wheel according to Embodiment 2 of the present invention, and the same or corresponding parts as those in FIG.
In the first embodiment, the tangent angle β1 of the blade 4 defined on the inner diameter side of the impeller 1 is two different tangent angles β11 and β12 for each of the blocks A and B. Then, by setting the tangent angle β2 of the blade 4 defined on the outer diameter side of the impeller 1 to two different tangent angles β21 and β22 for each of the blocks A and B, the airflow for each of the blocks A and B Each blade 4 is formed so that the blowing angle changes periodically.
[0015]
According to the second embodiment having such a configuration, the angle of the airflow blown out from the impeller 1 changes according to the tangent angle β2 of the blade 4 for each block A, B. For example, an upward airflow is formed when the block A is located on the side of the blowing air passage 7 in FIG. 3, and a downward airflow is formed when the block B is located on the side of the air blowing air passage 7. Due to such fluctuations in the direction of air flow, even if the diffuser enlargement ratio is increased, separation and backflow of the air flow are less likely to occur, the diffuser efficiency is improved, and the blowing power is reduced as in the case of the first embodiment. An effect is obtained.
[0016]
In the second embodiment as well, the tangent angle β2 of the blade 4 is not specified by the two types of tangent angles β21 and β22 that are different for each of the blocks A and B, but various types (at least two or more blades). The impeller 1 may be configured to have β2 of the same number as a plurality of blocks each having a single block. In this case, the same effect can be obtained. Furthermore, in the blade element (blade) shape of FIG. 5, the warp line is a single arc, the thickness is a uniform thickness distribution, and the blade tip shape is a semicircular arc, but the warp line, the thickness distribution, the blade tip shape, etc. Is not specified, and the same effect as in the second embodiment can be obtained by the circumferential distribution of the tangent angle β2 of the blade 4.
[0017]
Embodiment 3 FIG.
6 is a cross-sectional view showing a cross-flow fan wheel according to Embodiment 3 of the present invention. The same or corresponding parts as those in FIGS. 1 and 5 are denoted by the same reference numerals.
In the third embodiment, the blade 4 of the entire impeller 1 is divided into three blocks A, C, and D, and the tangent angle β1 of the blade 4 defined on the inner diameter side of the impeller 1 is set to each block A, C. , D, and three different tangent angles β11, β12, β13, and the tangential angle β2 of the blade 4 defined on the outer diameter side of the impeller 1 is different between the block A and the blocks C, D2. The tangent angles β21 and β22 of the kind are used, and the tangent angle on the outer diameter side of the block C and the block D is the same tangent angle β22.
[0018]
According to the third embodiment having such a configuration, the angle of the airflow blown out from the impeller 1 changes according to the combination of the tangent angles β1 and β2. For example, an upward airflow is formed when the block A is located on the side of the blowing air passage 7 in FIG. 3, and a downward airflow is formed when the block C is located on the side of the air blowing air passage 7. When the block D is positioned in the middle, a blowing airflow is formed in the middle. Due to such fluctuations in the blowing direction of the airflow, even if the diffuser enlargement rate is increased, the blown airflow is hardly separated or backflowed, and the static pressure recovery rate by the diffuser is improved, and the blowing power is reduced. Here, the control of the airflow blowing direction that can be performed only with the tangent angle β1 and the other types with only the tangential angle β2 is limited by the separation of the flow between the blades, the secondary flow, and the like. Thus, by combining the tangential angle β1 defined on the inner diameter side of the impeller 1 and the change of the tangential angle defined on the outer diameter side of the impeller 1 and β2, a wider range of airflow blowing directions can be obtained. There is an effect that control becomes possible.
[0019]
In the third embodiment, the impeller 1 composed of three types of inner diameter side tangent angles β1 (β11, β12, β13) and two types of outer diameter side tangent angles β2 (β21, β22) has been described. However, the types of the tangent angles β1 and β2 are not limited thereto, and the impeller 1 is configured to have more types (the same number as a plurality of blocks including at least two blades as one block) β1 and β2. In this case, the same effect can be obtained. Further, in the blade element (blade) shape of FIG. 6, the warp line is a single arc, the thickness is an equal thickness distribution, and the blade tip shape is a semicircular arc, but the warp line, the thickness distribution, the blade tip shape, etc. Is not specified, and the same effect as in the third embodiment can be obtained by the circumferential distribution of the tangent angles β1 and β2 of the blades 4.
[0020]
Embodiment 4 FIG.
FIG. 7 is a view showing a circumferential distribution of the blade tangent angle β1 of the once-through fan impeller according to Embodiment 4 of the present invention.
In the fourth embodiment, there are five types of blade tangent angles β1 defined on the inner diameter side of the impeller, and the five types of blades are distributed approximately periodically in the circumferential direction.
[0021]
According to the fourth embodiment, since the five kinds of tangent angles β1 of the blades are periodically distributed in the circumferential direction, the five kinds of tangent angles β1 are smoothed by the substantially periodic change. There is an effect that the loss of the secondary flow between the blades due to the rapid change of the airflow between the blades due to the change of the tangent angle β1 is reduced.
[0022]
Reference Example 1
FIG. 8 is a view showing the circumferential distribution of the blade tangent angle β1 of the once- through fan impeller according to Reference Example 1. FIG.
In Reference Example 1 , the type of blade tangent angle β1 defined on the inner diameter side of the impeller is increased as shown in FIG.
Thus, by increasing the type of the tangent angle β1 of the blade, there is an effect that the loss described in the fourth embodiment can be further reduced. In addition, although the change of (beta) 1 in FIG. 8 illustrated what was given by the period of 1 cycle per impeller circumference, a period, an amplitude (the swing width of (beta) 1), etc. are not restricted to this.
[0023]
Embodiment 5 FIG.
FIG. 9 is a diagram showing a circumferential distribution of the blade tangent angle β1 of the once-through fan wheel according to the fifth embodiment of the present invention.
In the fifth embodiment, there are three types of blade tangent angles β1 defined on the inner diameter side of the impeller, and the three types of tangent angles β1 are randomly distributed in the circumferential direction of the impeller. .
As described above, in the fifth embodiment, the three types of tangential angles β1 are randomly distributed in the circumferential direction, thereby amplifying the turbulence of the blown airflow and improving the diffusibility of the airflow and the boundary layer of the diffuser wall surface. There is an effect that the turbulent flow is promoted, and the separation and backflow on the wall surface are suppressed, thereby improving the diffuser efficiency.
[0024]
Reference Example 2
FIG. 10 is a diagram showing a circumferential distribution of the blade tangent angle β1 of the once-through fan impeller according to the reference example 2 .
In Reference Example 2 , the type of tangent angle β1 in the fifth embodiment is further increased. Thus, by further increasing the type of the tangent angle β1 of the fifth embodiment in the reference example 2 , there is an effect that the high-frequency turbulence component is increased and the diffusibility of the airflow is further increased.
[0025]
Embodiment 7 FIG.
FIG. 11 is a diagram showing a circumferential distribution of the blade tangent angle β2 of the once-through fan wheel according to the seventh embodiment of the present invention.
In Embodiment 7 , there are five types of blade tangent angles β2 defined on the outer diameter side of the impeller, and the five types of tangent angles β2 are changed approximately periodically in the circumferential direction of the impeller. The configuration is as follows.
According to the seventh embodiment, five types of tangent angles β2 are smoothly distributed due to a substantially periodic change, and the inter-blade secondary due to a sudden change in the inter-blade air path due to the change of the tangent angle β2. This has the effect of reducing the loss of flow and the like.
[0026]
Reference Example 3
FIG. 12 is a view showing the circumferential distribution of the blade tangent angle β2 of the once-through fan wheel according to the reference example 3 .
In this reference example 3 , the type of the tangent angle β2 according to the seventh embodiment is further increased. By increasing the type of the tangent angle β2, the loss such as the inter-blade secondary flow can be further reduced. In addition to this, there is an effect that the correlation between the pressure fluctuations caused by the interference between the outer periphery of the impeller and the stabilizer is lowered, and the rotational noise can be reduced.
In addition, although the change of the tangent angle β2 in FIG. 12 is exemplified by a cycle of two cycles per one wheel of the impeller, the cycle, amplitude (amplitude of the tangent angle β2), etc. are specified. Absent.
[0027]
Embodiment 8 FIG.
FIG. 13 is a diagram showing a circumferential distribution of the blade tangent angle β2 of the once-through fan wheel according to the eighth embodiment of the present invention.
In the eighth embodiment, there are three types of blade tangent angles β2 defined on the outer diameter side of the impeller, and the three types of tangent angles β2 are randomly changed in the circumferential direction of the impeller. This is a simple configuration.
According to the eighth embodiment, the three tangent angles β3 are randomly distributed in the circumferential direction, thereby amplifying the turbulence of the blown airflow and improving the airflow diffusivity and the boundary of the diffuser wall surface. There is an effect that the turbulent flow can be promoted and the diffuser efficiency can be increased by suppressing separation and backflow on the wall surface.
[0028]
Reference Example 4
FIG. 14 is a diagram showing a circumferential distribution of the blade tangent angle β2 of the once-through fan impeller according to the reference example 4 .
In this reference example 4 , the type of the tangent angle β2 according to the eighth embodiment is further increased, and the increase in the type of the tangent angle β2 increases the high-frequency turbulence component and further improves the diffusibility of the airflow. At the same time, the correlation between the pressure fluctuations caused by the interference between the outer periphery of the impeller and the stabilizer is broken, so that the rotating sound can be reduced.
[0029]
Ninth Embodiment
In Embodiment 9 of the present invention, the blade to provide a substantially periodic modulation of the tangential angle β1 of the blade, as shown in FIG. 7, the substantially periodic modulation of the tangential angle β2, as shown in FIG. 1 1, respectively It is a car.
According to the ninth embodiment, a synergistic effect between controllability and rotation noise reduction can be obtained in the air flow blowing direction.
In the Figure 7 and Figure 1 1, the tangent angle .beta.1, although the modulation phase of β2 been exemplified those the same phase, each modulation phase, period, amplitude is not intended to be identified.
[0030]
Embodiment 10 FIG.
Tangent angle β1 of the blades of the impeller according to a tenth embodiment of the present invention is applied to FIG. 9 and Figure 1 3 to illustrate the circumferential distribution of .beta.2.
In this tenth embodiment, to configure the impeller to provide a random modulation of the tangential angle β1 of the blade, as shown in FIG. 9, the random modulation of the tangential angle β2 of the blade, as shown in FIG. 1 3, respectively Is.
According to the tenth embodiment, it is possible to obtain a synergistic effect between the controllability of the airflow blowing direction and the reduction of the rotational sound.
[0031]
Embodiment 11 FIG.
Tangent angle β1 of the blades of the impeller according to Embodiment 11 of the present invention is applied to FIG. 7 and Figure 1 3 to illustrate the circumferential distribution of .beta.2.
Impeller according the eleventh embodiment, as impart a substantially periodic modulation of the tangential angle β1 of the blade, as shown in FIG. 7, the random modulation of the tangential angle β2 of the blade, as shown in FIG. 1 3, respectively It is composed.
According to such an eleventh embodiment, it is possible to obtain a synergistic effect of controllability in the air flow blowing direction and reduction of rotational sound.
[0032]
Embodiment 12 FIG.
FIGS. 9 to 11 are applied to describe the circumferential distribution of the tangent angles β1 and β2 of the impeller blades according to the twelfth embodiment of the present invention.
Impeller according twelfth embodiment is to provide a random modulation of the tangential angle β1 of the blade, as shown in FIG. 9, the substantially periodic modulation of the tangential angle β2 of the blade, as shown in FIG. 1 1, respectively It is composed.
In the case of the twelfth embodiment as described above, a synergistic effect between controllability in the air flow blowing direction and reduction of the rotational sound can be obtained.
[0033]
Embodiment 13 FIG.
FIG. 15 is a sectional view showing an air conditioner according to Embodiment 13 of the present invention. The air conditioner includes a casing 5, a stabilizer 6, a blowout air passage 7, an air suction port 8, and an indoor unit. 9 and a heat exchanger 10, and the impeller 1 according to the first to twelfth embodiments is incorporated.
In such an air conditioner according to the thirteenth embodiment, even if the enlargement ratio of the diffuser composed of the casing 5 and the stabilizer 6 is increased, the backflow of the blown airflow hardly occurs and the blowing power is not reduced. Can be greatly reduced.
[0034]
【The invention's effect】
As described above, according to the present invention, a plurality of blades arranged around the axis of the rotation shaft and parallel to the rotation shaft are provided, and the arrangement group of the blades is divided into a plurality of blocks on a cross section perpendicular to the rotation shaft. And each block is composed of at least two blades and the blade tangent angle β1 defined on the inner diameter side of the impeller or the blade tangent angle β2 defined on the outer diameter side of the impeller Alternatively, both tangent angles β1 and β2 are set to different tangent angles for each block, and the same tangent angle is used in the block, so that the direction of air flow when the impeller rotates changes for each block, and the diffuser efficiency Is improved, and the blast power is reduced.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing a once-through blower impeller according to Embodiment 1 of the present invention.
FIG. 2 is a front view of FIG.
FIG. 3 is an operation explanatory diagram showing an air flow blowing direction when the impeller rotates.
FIG. 4 is a diagram showing a ratio of a diffuser expansion ratio between a conventional impeller and an impeller of the present invention and a blowing power at the same air volume.
FIG. 5 is a cross-sectional view showing a once-through blower impeller according to Embodiment 2 of the present invention.
FIG. 6 is a sectional view showing a once-through fan wheel according to a third embodiment of the present invention.
FIG. 7 is a diagram showing a circumferential distribution of a blade tangent angle β1 of a once-through blower impeller according to Embodiment 4 of the present invention.
8 is a diagram showing a circumferential distribution of a blade tangent angle β1 of the once- through blower impeller according to Reference Example 1. FIG.
FIG. 9 is a diagram showing a circumferential distribution of a blade tangent angle β1 of a once-through blower impeller according to Embodiment 5 of the present invention.
10 is a diagram showing a circumferential distribution of a blade tangent angle β1 of the once-through blower impeller according to Reference Example 2. FIG.
FIG. 11 is a diagram showing a circumferential distribution of a blade tangent angle β2 of a once-through fan wheel according to a seventh embodiment of the present invention.
12 is a view showing a circumferential distribution of a blade tangent angle β2 of the once-through blower impeller according to Reference Example 3. FIG.
FIG. 13 is a diagram showing a circumferential distribution of a blade tangent angle β2 of a once-through fan wheel according to an eighth embodiment of the present invention.
14 is a view showing a circumferential distribution of a blade tangent angle β2 of the once-through blower impeller according to Reference Example 4. FIG.
FIG. 15 is a sectional view showing an air conditioner according to Embodiment 13 of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Impeller, 2 Rotating shaft, 3 Partition plate, 4 Blades, 5 Air conditioner casing, 6 Stabilizer, 7 Outlet air passage, 8 Air inlet, 9 Indoor unit, 10 Heat exchanger, AD Block of blade .

Claims (9)

In the once-through blower impeller having a plurality of blades arranged around the axis of the rotation axis and parallel to the rotation axis,
The arrangement group of the blades is divided into a plurality of blocks on a cross section perpendicular to the rotation axis, and each block is composed of at least two blades, and the blades are defined on the inner diameter side of the impeller. Both the tangent angle β1 or the tangent angle β2 of the blade defined on the outer diameter side of the impeller or the tangential angles β1 and β2 are different tangent angles for each block, and the same tangent angle in the block A once-through fan wheel characterized by that. Flow blower impeller of claim 1, wherein the circumferential distribution of the tangent angle β1 of the blades were substantially cyclically modulated. Flow blower impeller according to claim 1, characterized in that randomly modifying its circumferential distribution of the tangent angle β1 of the blade. Flow blower impeller of claim 1, wherein the circumferential distribution of the tangent angle β2 of the blade was approximately cyclically modulated. Flow blower impeller according to claim 1, characterized in that randomly modifying its circumferential distribution of the tangent angle β2 of the blade. Flow blower impeller according to claim 1, characterized in that substantially cyclically modulated circumferential distribution of the tangent angle β1 and β2 of the blade. Flow blower impeller according to claim 1, characterized in that randomly modifying its circumferential distribution of the tangent angle β1 and β2 of the blade. Circumferentially distributed substantially cyclically modulated to, and once-through blower impeller according to claim 1, characterized in that by modulating the circumferential distribution of the tangent angle β2 of the blade randomly tangential angle β1 of the blade. Circumferentially distributed randomly modifying its, and once-through blower impeller of claim 1, wherein the circumferential distribution of the tangent angle β2 of the blade was approximately cyclically modulated tangential angle β1 of the blade.

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