CN1297751C - Impeller for fun, fun therewith and air conditioner with the fun - Google Patents

Abstract

An impeller for a blower, including a hub and two blades arranged on the hub, each blade is symmetrical to each other with the hub as the center, when the chord length of the blade at the position of the representative mean square radius "Rr" of each blade is "L" When the representative actual length in the radial direction is "b", the aspect ratio "b/L" of each blade has a shape in the range of "b/L≤1". The portion from the vicinity of the position of the radius to the position on the tip side of the outer periphery has a curved streamline shape that is concave with respect to the upper side of the wind, and the portion from the vicinity of the position representing the mean square radius of the blade to the position on the hub side has a streamlined shape with respect to the upper side of the wind. It is a convex curve shape. Due to the rotation of each blade, each blade allows air to flow in from the leading edge of each blade and flow out from the trailing edge. The blade end vortex generated on the negative pressure surface of each blade is stripped and flowed away from the blade. The spacing between the blades is sufficiently wide to avoid the influence of blade tip vortices.

Description

Impellers for blowers, blowers using impellers, and air conditioners using blowers

(1) Technical field

The present invention relates to an impeller for a blower, a blower using the impeller, and an air conditioner using the blower.

(2) Background technology

FIG. 15 shows a plan view of an impeller of a conventional diagonal-flow blower, and FIG. 15 shows a diagram of a rotation track of the impeller. In the impeller using such an oblique flow blower, gas flows obliquely with respect to the rotary shaft inside the impeller. That is, in FIG. 15 , the impeller 18 of the diagonal flow blower includes a substantially conical trapezoidal hub 20 and a plurality of blades 19 provided on the hub 20 . The rotation track diagram of the impeller 18 is shown in FIG. 14 . The air blower includes the impeller 18, a casing for accommodating the impeller 18, a rotating shaft combined with a hub 20, and a motor. The impeller 18 is rotated by the motor to generate air blowing. When the aspect ratio "b/L" of the ratio of the chord length L of the blade at the representative mean square radius position of the blade 19 to the actual length b in the radial direction of the blade is less than 1, that is, when "b/L≤ In the range of 1", in order to obtain sufficient static pressure, the number of blades 19 should be at least three or more. Furthermore, the leading edge 21 of the blade 19 has a curved shape such as a logarithmic spiral.

However, in the above-mentioned conventional structure, when the aspect ratio "b/L" is less than 1 (that is, the range of "b/L≤1"), in the structure of the impeller having at least three blades 19, the rotation A blade end vortex 19D as shown in the figure is generated near the outer periphery of the blade 19 along the direction of the arrow. The blade end vortex 19D is separated from the blade 19 and has a great influence on the state of the incoming air in the rear blade 19 . That is, the rear blade 19 is greatly affected by the blade tip vortex 19D that is separated from the front blade, and the rear blade 19 receives the greatly turbulent inflow air to perform aerodynamic operation. Therefore, due to the influence of the blade end vortex 19D, there is a limit to noise reduction and improvement of static pressure characteristics.

Moreover, the larger the number of blades 19, the larger the volume occupied by the impeller, so the manufacturing cost of the impeller must be high.

(3) Contents of the invention

The object of the present invention is to reduce the noise of the impeller for blower, increase the static pressure and reduce the manufacturing cost of the impeller.

The invention provides an impeller for a blower, which includes a hub and two blades arranged on the hub, each blade of the two blades is arranged symmetrically with the hub as the center, when each blade of the two blades When the chord length of the blade at the representative mean square radius "Rr" position is "L" and the representative actual length in the radial direction is "b", the aspect ratio "b/L" of each blade has "b/L≤1" The shape of the range is characterized in that, in the radial section of each of the blades, the portion from the vicinity of the position representing the mean square radius of the blade to the tip side of the outer circumference has a concave curve with respect to the upper side of the wind The shape is streamlined, and the portion from the vicinity of the position representing the mean square radius of the blade to the position on the hub side has a convex curved shape with respect to the upper side of the wind. Inflow from the leading edge of each blade, and flow out from the trailing edge, the blade end vortex generated on the negative pressure surface of each blade is stripped and flowed away from the blade, and the interval between each blade is sufficiently wide to avoid is affected by the blade tip vortices.

The present invention also provides a blower, which includes a motor and an impeller connected to the motor, the impeller includes a hub and two blades arranged on the hub, and each blade of the two blades is set to use the hub as a The centers are symmetrical to each other. When the chord length of the blade at the position of the representative mean square radius "Rr" of the two blades is "L" and the representative actual length in the radial direction is "b", the The aspect ratio "b/L" has a shape in the range of "b/L≤1", and in the radial section of each of the blades, the portion from the vicinity of the position representing the mean square radius of the blade to the position on the outer peripheral tip side of the blade has The curved streamline shape is concave (2a) on the windward side, and the portion from the vicinity of the position representing the mean square radius of the blade to the position on the hub side has a convex curved shape on the windward side.

The present invention also provides an air conditioner including an indoor unit, an outdoor unit, and piping provided between the indoor unit and the outdoor unit. The outdoor unit has a heat exchanger and a blower. The blower has a motor and a motor connected to the motor. The impeller comprises a hub and 2 blades arranged on the hub, each blade of the 2 blades is arranged symmetrically with the hub as the center, and the mean square of each blade of the 2 blades is When the chord length of the blade at the radius "Rr" position is "L" and the representative actual length in the radial direction is "b", the aspect ratio "b/L" of each blade has a range of "b/L≤1" The shape is characterized in that, in the radial cross-section of each of the blades, the portion from the vicinity of the position representing the mean square radius of the blade to the position on the tip side of the outer periphery has a streamlined curved shape that is concave with respect to the windward side , the portion from the vicinity of the position representing the mean square radius of the blade to the position on the hub side has a curved shape that is convex relative to the windward side.

Preferably, the two blades are arranged symmetrically with respect to the center of the hub.

The air blower of the present invention includes a motor and an impeller connected to the motor, and is characterized in that the impeller has the same structure as the aforementioned impeller.

The air conditioner of the present invention includes an indoor unit, an outdoor unit, and piping provided between the indoor unit and the outdoor unit, the outdoor unit has a heat exchanger and a blower, the blower has a motor and an impeller connected to the motor, and is characterized in that The aforementioned impeller has the same structure as the aforementioned impeller.

With the above structure, since the distance between the two blades is sufficiently wide, the blade end vortex of the air generated on the negative pressure surface near the outer circumference of the rotating blade is separated from the blade and flows away, reducing the impact on the rear of the rotating blade. The influence of the state of the blade's inflow air. Furthermore, the turbulence of the air flowing into each blade is reduced. Inflow air into each blade is smooth. Instabilities such as air stripping and stalling on the rear blades during rotation are less likely to occur. Therefore, the noise in the blade can be reduced and the static pressure can be increased.

In addition, the impeller with two blades can reduce the volume occupied by the impeller compared with the impeller with more than three blades, thereby reducing the manufacturing cost of the impeller.

(4) Description of drawings

FIG. 1 is a diagram showing a locus of rotation of an impeller of a diagonal flow blower using an impeller for a blower according to an embodiment of the present invention.

Fig. 2 is a plan view showing an impeller for a blower according to an embodiment of the present invention.

Fig. 3 is a developed view of a fan impeller according to an embodiment of the present invention, which is cut and developed at a position representing a mean square radius, and a thick blade is applied.

Fig. 4 is a blade development diagram showing a fan impeller according to an embodiment of the present invention, which is cut and unfolded at a position representing a mean square radius, and thin blades having a certain thickness are applied.

Fig. 5 is a schematic view showing the operation of the blower impeller according to one embodiment of the present invention.

Fig. 6 is a characteristic diagram showing the relationship between the aspect ratio "b/L" of the blower impeller and the air volume at a blowing noise of 41 dB according to an embodiment of the present invention.

Fig. 7 is a characteristic diagram comparing experimental values of static pressure characteristics of a blower impeller having two blades in an embodiment of the present invention and a conventional blower impeller having three blades.

Fig. 8 is a diagram showing the locus of rotation of the impeller in Example 1 in which the fan impeller according to one embodiment of the present invention is used in an axial flow fan.

Fig. 9 is a plan view showing a blower impeller according to an embodiment of the present invention used in an impeller of an axial flow blower.

Fig. 10 is a cross-sectional view in the radial direction of the impeller of Example 2 in which the fan impeller according to one embodiment of the present invention is used in a diagonal flow fan.

FIG. 11 is a graph showing experimental results of the noise spectrum of the blower impeller of Example 2. FIG.

Fig. 12 is a plan view showing the motion of the vortex at the blade end of the impeller of Example 3 in which the fan impeller according to one embodiment of the present invention is used in a diagonal flow type fan.

Fig. 13 is a schematic diagram of an air conditioner using a blower having an impeller according to an embodiment of the present invention.

Fig. 14 is a plan view showing a conventional fan impeller.

Fig. 15 is a diagram showing a rotation locus of an impeller for a conventional air blower.

(5) specific implementation

An impeller for a blower according to an embodiment of the present invention includes a hub and two blades arranged on the hub. When the representative actual length of the radial direction of the blade is "b", the aspect ratio is expressed as the ratio "b/L", which is characterized in that each of the above-mentioned blades has a shape in the range of "b/L≤1"; preferably the above-mentioned The two blades are arranged symmetrically with respect to the center of the hub.

With the above-mentioned structure, since the distance between the two blades is sufficiently wide, the blade-end vortex of the air generated on the negative pressure surface near the outer periphery of the rotating blade is separated from the blade and flows away, facing the rotating rear blade. The influence of the state of the inflow air is reduced. In this way, the two blades are not mutually affected by the vortex at the blade end. Therefore, the turbulence of the inflow air received by each blade is reduced, and the inflow air entering each blade is smooth. Therefore, unstable phenomena such as air stripping and stall are less likely to occur in each blade.

In addition, the above impeller with 2 blades is smaller than the impeller with 3 or 4 blades.

Preferably, in the radial section of each of the blades, the part from the vicinity of the representative mean square radius position of the blade to the outer peripheral position has a concave curved shape relative to the upper side of the wind, and from the vicinity of the representative mean square radius position of the blade to the outer peripheral position. The portion on the hub side has a convex curved shape with respect to the windward side.

With the above structure, since the blade has a concave curved shape, the blade itself is streamlined with respect to the rotation direction of the blade. Therefore, even when the number of blades is two, the "nZ" sound as the blade rotation noise is lower than the sound pressure level of the turbulent flow noise. As a result, abnormal noise as a whole impeller is prevented from occurring. And it actually sounds good.

Preferably, one point of the triangular auxiliary vane is overlapped at the intersection of the leading edge and the outer periphery of the vane, and is in close contact with the leading edge to form one side of the triangular auxiliary vane. Thus, the triangular auxiliary blades are provided as blades of the main blades.

With the above structure, starting from the tip of the triangular-shaped blade, the blade-end vortex is conically generated on the negative pressure surface of the blade, and the blade-end vortex is separated and flowed away in the middle of the blade. The triangular-shaped blade has the function of defining a blade-tip vortex at its front end. Therefore, the triangular blade defines the state in which the blade tip vortex occurs on the negative pressure surface near the outer periphery of the blade and the state in which the blade tip vortex separates from the blade and flows away. Therefore, the triangular-shaped blade has an effect of minimizing the influence of the blade-end vortex of the turning rear blade. Therefore, even in the impeller having two blades with sufficiently wide intervals between the blades, the state of the inflow air of the rear blade that is turned next can be made smooth and optimal with less turbulence. In addition, the rear blade is less affected by the blade tip vortex, the inflow air entering each blade is the smoothest, and it is more difficult for the rear blade to generate unstable phenomena such as air stripping and stalling.

Preferably, the air blower provided with the impeller is installed in an outdoor unit of an air conditioner provided with a heat exchanger.

By adopting the above structure, the noise of the outdoor unit is small during operation, the manufacturing cost can be reduced, and the design becomes easy.

Typical embodiments of the present invention will be described below with reference to FIGS. 1 to 13 .

Typical embodiment 1:

1 to 9 show an impeller for a fan according to a typical embodiment of the present invention. Among them, FIG. 1 is a diagram of the rotation trajectory of the impeller used in the diagonal flow blower. Fig. 2 is a plan view of the impeller of the diagonal flow blower. Fig. 3 is a developed view showing a section of an impeller for a blower according to an embodiment of the present invention at a position representing a mean square radius. In Figure 3, the blades have thick blades. Fig. 4 is a diagram showing the impeller of the blower after being cut at a position representing the mean square radius, and it is suitable for the occasion where the blade is a thin blade with a certain thickness. Fig. 5 is a schematic view showing the operation state of the impeller used in the blower. Fig. 6 is a characteristic diagram showing a characteristic experiment of the performance of the blower impeller, the horizontal axis represents the aspect ratio "b/L", and the vertical axis represents the air volume at which the blowing noise is 41db. 7 is a characteristic diagram comparing the static pressure characteristics of the fan impeller having two blades of the present exemplary embodiment and the conventional three-blade impeller for a fan. Fig. 8 is a diagram showing a locus of rotation of an impeller for a blower used in an axial flow blower. Fig. 9 is a plan view of an impeller of an axial fan.

In Fig. 1, an impeller 1 for a diagonal flow blower includes a substantially conical trapezoidal hub 3 and two blades 2 provided on the outer peripheral surface of the hub 3. The two blades 2 have the same shape as each other, and each blade 2 is set in relative positions. That is, the blades 2 are arranged at positions symmetrical to each other with the hub 3 as the center. When the chord length of the above-mentioned blades 2 at the position of the representative mean square radius of the blade is "L", and the representative actual length of the above-mentioned blades in the radial direction is "b", the ratio "b/L" represents the span Compare. The aspect ratio is equal to or less than 1. That is, the aspect ratio is set in the range of "b/L≦1". And two blades 2 having an aspect ratio set within this range are provided.

The above structure will be further described below.

The above-mentioned hub 3 is trapezoidal with a circular cross section. When the minimum radius of the circle of the above-mentioned hub 3 is "r1" and the maximum radius of the above-mentioned hub is "r2", if the representative hub radius is "r", it is defined as r=(r1+r2)/2.

The distance from the center of the above-mentioned hub to the largest front end of the above-mentioned blade is "R2", and the distance from the center of the above-mentioned hub to the smallest front end of the above-mentioned blade is "R1". If the representative hub radius of the impeller is "R", then Defined as R=(R1+R2)/2.

When the representative mean square radius is "Rr", it is defined as Rr=((R ² +r ² )/2) ^1/2 . The above-mentioned "L" is the chord length of the above-mentioned blade at the position of the above-mentioned representative mean square radius "Rr".

In Fig. 1, the center line 31C-31C of the impeller 1 is taken as the center line, and the vertex passing through the cone with the mean square radius "Rr" is "P1". Figures 3 and 4 show an expanded view of the blade 2 sectioned along the line 32A-32A of the cone. The chord length of the blade 2 is "L". This line 32A-32A is represented as a curve 32A-32A in FIG. 2 as a plan view. In FIG. 1 , the representative actual length "b" of the blade 2 in the radial direction is the actual length in the spanwise direction of the blade 2 connecting the position representing the hub radius "r" and the position representing the radius "R".

As shown in FIG. 5 , the shafts of the electric motors 12 are fixed in the hub 3 and they are accommodated in a suitable housing 11 . The impeller 1 is rotated by the motor 12 to produce air blowing as shown by the arrow. At this point, almost all the air in FIG. 1 flows into the leading edge 4 of the blade 2 and flows out from the trailing edge 5 . Thus, the impeller 1 performs aerodynamic work.

In Fig. 1, the oblique flow fan uses the ratio "b/L" of the chord length "L" at the representative mean square radius position of the impeller 1 and the representative actual length "b" of the blade in the radial direction to represent the aspect ratio.

6 is a characteristic diagram showing the relationship between the aspect ratio "b/L" of an impeller having two blades and the air volume at a blowing noise of 41 dB. Fig. 6 is based on experimental data of an impeller 1 having a diameter (φ) of 415 mm.

It can be seen from Fig. 6 that when the aspect ratio is in the range of "b/L≤1", the wind noise is saturated at 41dB. However, when the aspect ratio is in the range of "b/L≥1", the air volume will decrease sharply.

The impeller 1 for a diagonal flow fan according to this exemplary embodiment has two blades 2 provided on a hub 3 . The chord length "L" of the blade 2 at the representative mean square radius position of the blade 2 and the representative actual length "b" of the radial direction of the blade 2 are set as the aspect ratio "b/L" in "b/L≤1" range, and the impeller 1 has two blades with the above-mentioned aspect ratio. The chord length on the outer peripheral side of the blade is longer than the chord length on the hub side.

With the above structure, in the impeller with the blades having an aspect ratio in the range of "b/L≤1", since the interval between the blades 2 is sufficiently wide, the negative pressure surface near the outer periphery of each blade 2 (that is, near the blade tip 6) The blade end vortex 33D generated on the blade 8 is stripped and flowed away from the blade 2, and has very little influence on the state of the inflow air of the rear blade 2 that turns around. Therefore, the blades 2 are not mutually affected by the blade-end vortex 33D. Therefore, the inflow air that each blade 2 enters has little turbulence, and each blade 2 receives smooth inflow air. Therefore, unstable phenomena such as detachment and stall are less likely to occur on the blade 2 . Thereby, the air volume of the impeller 1 at the same noise level is increased. Data to demonstrate this is shown in FIG. 6 . FIG. 6 is a characteristic diagram showing the impeller 1 of the above-mentioned diagonal flow blower.

In addition, since the blade-end vortex 33D of the rotating front blade has little influence on the rear blade 2, unstable phenomena such as detachment or stall are unlikely to occur on the rear blade 2, thereby improving the static pressure characteristics of the impeller 1. Fig. 7 shows characteristic curves comparing the static pressure characteristics of an impeller having two blades and an impeller having three blades among the impellers of a diagonal flow blower. Fig. 7 shows the static pressure characteristics when the impeller for a diagonal flow blower with a diameter of 415 mm in diameter operates at a rotational speed of 712 rpm and the open air volume point is 29.5 cubic meters per minute. The open air volume point is the air volume at zero static pressure. In the range from the open air volume point to the air volume point "Q1", the impeller with 2 blades shows a slightly stronger static pressure than the impeller with 3 blades. In the range from the air volume point "Q1" to the air volume point "Q2", the impeller having two blades and the impeller having three blades have the same static pressure as each other. In the range from the air volume point "Q2" to the closed air volume point (the point where the air volume is 0), the impeller with 3 blades exhibits stronger static pressure than the impeller with 2 blades. A blower used for an air conditioner is generally used in a range from an open air volume point to an air volume point "Q2" vicinity at the time of heating. Only during the heating operation in which frost is formed on the heat exchanger significantly, it operates in the range from the air flow point "Q2" to the closed air flow point (the air flow is 0), and the defrosting operation does not occur frequently. Therefore, the performance in the range from the vicinity of the air flow point "Q2" of the blower used in the air conditioner to the closed air flow point has little significance in terms of machine design. Therefore, in the range from the air volume point "Q2" to the closed air volume point (the point where the air volume is 0), the impeller with 3 blades exhibits slightly stronger static pressure performance than the impeller with 2 blades. It is not a problem in the blower of the machine.

Also, an impeller with 2 blades takes up less volume than an impeller with 3 or 4 blades. Therefore, the manufacturing cost of the impeller must be lower.

In addition, in Fig. 1, the centerline 31C-31C of the impeller is taken as the centerline, and the vertex of the 32A-32A line passing through the cone with the mean square radius "Rr" is "P1". Expansion of the blade sectioned by the line 32A-32A of the cone. FIG. 3 shows a blade with a thick blade 7 . In FIG. 3 , among the cross-sectional shapes of the blade 7 , the leading edge 4 of the blade 7 has an arc shape, and the trailing edge 5 has a tapered shape. The blade 7 has a pressure surface 9 and a suction surface 8 . In FIG. 3 , each of the blades has an arc-shaped leading edge 4 and a tapered trailing edge 5 , and has a shape gradually thickened from the trailing edge to the leading edge.

FIG. 4 shows a blade with a thin blade 10 . In FIG. 4 , the blade 10 has a thin section shape with a certain thickness. That is, the shape from the rear edge to the front edge has substantially the same thickness. The blade 10 has a pressure surface 9a and a suction surface 8a. The pressure surface 9a is located on the upper side of the wind, and the negative pressure surface 8a is located on the upper side of the wind.

An axial fan will be described below as an impeller for a fan according to another typical embodiment of the present invention. Fig. 8 shows the rotation track diagram of the impeller in the axial flow blower, and Fig. 9 shows its top view. In FIGS. 8 and 9 , the impeller 15 has two blades 14 . Here, the position representing the mean square radius "Rr" is indicated by the line 34B-34B. Even in the impeller 15 of the axial flow fan, the aspect ratio which is the ratio of the chord length "L" of the blade 14 representing the mean square radius position of the blade 14 to the actual length "b" of the blade 14 in the radial direction is "b/L" is also set in the range of "b/L≦1". Two blades having an aspect ratio set in the above-mentioned range are provided on the hub 13 .

The impeller of the axial flow blower having the above structure has the same function and effect as the impeller of the above diagonal flow blower.

Typical embodiment 2:

Fig. 10 is a cross-sectional view in the radial direction of the impeller of the oblique flow blower according to the exemplary embodiment 2 of the present invention. Although FIG. 10 shows a sectional view in the radial direction along line 35B-35B in FIG. 2 , the blades of the impeller of the present exemplary embodiment 2 are different from the blades of the impeller of exemplary embodiment 1. FIG. 11 shows the noise spectrum of the impeller of the oblique flow blower according to the exemplary embodiment 2. FIG.

Compared with the impeller of typical embodiment 1, the impeller of typical embodiment 2 of the present invention is only different in blade shape, and other structures are the same. Therefore, all the parts with the same structure and the same function and effect as those of the typical embodiment 1 are given the same reference numerals, and the specific description is omitted, and the description will focus on the different parts.

The shape from the vicinity of the line 36A-36A representing the mean square radius "Rr" passing through the blade 2 to the position on the blade tip 6 side has a curved shape that is concave 2a with respect to the upper side of the wind, and from the vicinity of the line 36A-36A passing through the representative mean square radius "Rr" The shape from the vicinity of the line 36A-36A to the hub 3 side has a curved shape that is convex 2b with respect to the windward side. And two blades 2 having such a shape are arranged on the hub 3 . The two blades 2 are arranged symmetrically with respect to the center of the hub 3 . Each blade 2 has a negative pressure surface 8b and a pressure surface 9b. The impeller 16 has two blades 2 of this shape. The impeller 16 is used for a diagonal flow blower.

With the above-mentioned structure, since the shape from the vicinity of the line 36A-36A representing the mean square radius "Rr" passing through the blade 2 to the position on the outer peripheral side is a concave curved shape with respect to the upper side of the wind, the blade 2 itself is relative to the impeller. The direction of rotation of 16 is streamlined. Therefore, even if the number of blades is two blades, the "nZ" sound which is the rotation noise of the blade 2 is lower than the sound pressure level of the turbulent flow noise. Therefore, it is possible to prevent the occurrence of abnormal sound as a whole of the impeller 16, and the actual sense of hearing is good. This effect can be understood from the noise spectrum in FIG. 11 .

Fig. 11 shows the noise spectrum when the impeller of the oblique flow blower shown in Fig. 10 is driven at a speed of 720 rpm and the air volume is 29.8 cubic meters per minute. The impeller 16 including the blades 2 has a diameter of φ415 mm. The blade has a blade shape with an arcuate leading edge and a tapered trailing edge.

The sound pressure level near 1 kHz is turbulent noise. The 1nZ sound and its high-order harmonic components 2nZ, 3nZ, and 4nZ sound are the rotary noise of the blade 2 . It can be seen from Fig. 11 that, compared with the sound pressure level near 1kHz as the turbulent noise, the sound pressure level of the blade 2 rotating noise 1nZ and its higher harmonic components 2nZ, 3nZ, 4nZ is lower.

In addition, although this exemplary embodiment 2 has described the impeller used for the diagonal flow blower, the same effect as above can be obtained also for the impeller used for the axial flow blower.

Typical embodiment 3:

Fig. 12 is a top view of the impeller of the diagonal flow blower according to the exemplary embodiment 3.

The impeller of the exemplary embodiment 3 is different from the impeller of the exemplary embodiment 1 only in the shape of the blades, and the other structures are the same. Therefore, all the parts with the same structure and the same function and effect as those of the typical embodiment 1 are given the same reference numerals, and the specific description is omitted, and the description will focus on the different parts.

In FIG. 12 , one point of the triangular auxiliary blade 17 coincides with the intersection point of the leading edge 4 of the blade 2 which is the main blade, and the blade tip 6 . Furthermore, one side of the triangular auxiliary blade 17 is integrally provided in close contact with the front edge 4 of the blade 2 . Two blades 2 having such triangular auxiliary blades 17 are provided on the hub 3 . Each blade 2 is arranged symmetrically with the hub 3 as the center. In this way, the impeller 40 of the diagonal flow blower is constituted.

With the above configuration, the blade end vortex 33D is conically generated on the negative pressure surface of the blade 2 starting from the tip of the triangular auxiliary blade 17 , and the blade end vortex 33D is separated in the middle of the blade and flows away.

The tip of the triangular auxiliary blade 17 functions to regulate the generation of the blade tip vortex 33D. Therefore, the basics of the state where the blade tip vortex 33D occurs on the negative pressure surface in the vicinity of the blade tip 6 of the blade 2 and the state where it is separated from the blade 2 and flows away are defined. Therefore, the influence of the blade-end vortex 33D on the blade 2 turned backward is minimized. Therefore, it is a blade having an aspect ratio in the range of "b/L≤1", even if the distance between the two blades 2 is sufficiently wide, the inflowing air of the rear blade 2 that turns next can be reduced. Control remains less turbulent, allowing smooth optimum inflow air into the rear blades. Since the blade 2 at the rear is more difficult to be affected by the blade end vortex 33D, the inflow air entering each blade is the smoothest, and it is more difficult for the blade 2 to generate unstable phenomena such as air stripping and stall. The result is a further reduction in blade noise and a further increase in static pressure.

In addition, although the present exemplary embodiment 3 is described with respect to the impeller used for the diagonal flow blower, the same effect as above can be obtained also for the impeller used for the axial flow blower.

Typical embodiment 4:

Fig. 13 shows an air conditioner of a typical embodiment of the present invention.

In FIG. 13 , an air conditioner 50 includes an indoor unit 51 installed indoors, an outdoor unit 52 installed outdoors, and a circulation pipe 53 installed between the indoor unit 51 and the outdoor unit 52 . The indoor unit 51, the outdoor unit 52, and the circulation piping 53 form a refrigerant refrigeration cycle.

The outdoor unit 52 has a heat exchanger 54 and a blower 55 . The blower 55 has an impeller 56 . As the impeller 56, the impeller 1, the impeller 15, the impeller 16, or the impeller 40 described in the foregoing exemplary embodiment 1 can be used. The air blower 55 has an air blowing function for exchanging heat in the heat exchanger 54 .

That is, the air blower 55 sends air to the heat exchanger 54 . Alternatively, the air blower 55 has a function of forcibly moving heat near the heat exchanger 54 .

In the air conditioner 50 of this exemplary embodiment, the noise generated by the air blower 55 can be remarkably reduced compared with an air conditioner using a conventional air blower. And can improve air supply performance and heat exchange performance. In addition, manufacturing costs can be reduced.

That is, since the two blades are not mutually affected by the blade tip vortex of the other blade, the inflow air entering each blade is less turbulent and smooth, and unstable phenomena such as separation and stall on the blades are less likely to occur. As a result, the noise generated by the blades is significantly reduced and the static pressure is increased; in addition, the volume occupied by the impeller can be reduced, and the manufacturing cost can be reduced.

In addition, the "nZ" sound and its high-order harmonics, which are the rotation noise of the blade, are also lower than the sound pressure level of the turbulent flow noise. Therefore, it is possible to prevent the occurrence of abnormal sound as a whole of the impeller, and the actual sense of hearing is good.

In addition, since the blade has triangular auxiliary blades, the above-mentioned effect is further enhanced.

In addition, with the structure of the air conditioner of the present invention, the noise generated by the outdoor unit can be lower than that of conventional air conditioners. Furthermore, the air supply performance and heat exchange performance of the air conditioner can be improved. And can get cheap air conditioner.

Claims (20)

1. blower-use impeller comprises wheel hub (3,13) and is arranged at 2 pieces of blades (2,14) on this wheel hub,

Each blade of described 2 pieces of blades is that the center is symmetrically set with described wheel hub,

When the chord length of the blade of the representative mean square radius of gyration " Rr " position of each blade of described 2 pieces of blades is the representative physical length of " L " and radial direction during for " b ",

The aspect ratio of each blade " b/L " has the shape of " b/L≤1 " scope, it is characterized in that, in the radial direction cross section of described each blade, from having with respect to the wind upside to the part of the most advanced and sophisticated side position of periphery near the position of the representative mean square radius of gyration of described blade is curve shape streamlined of spill (2a)

From having with respect to the wind upside to the part of the position of hub side near the position of the representative mean square radius of gyration of described blade is the curve shape of convex (2b),

Because the rotation of described each blade, described each blade make air flow into from the leading edge (4) of described each blade, and flow out from trailing edge (5),

Go up the blade end eddy current (33D) that produces at the suction surface of described each blade (8,8a, 8b) and peel off diffluence from described blade,

Interval between each blade is fully wide, to avoid being subjected to the influence of described blade end eddy current (33D).

2. blower-use impeller as claimed in claim 1, it is characterized in that, described each blade has leg-of-mutton auxiliary blade (17), and 1 leading edge at described blade of described auxiliary blade overlaps with the intersection point place of periphery, and 1 limit and the described leading edge of described auxiliary blade are close to formation.

3. blower-use impeller as claimed in claim 1 is characterized in that the chord length of the outer circumferential side of described each blade is longer than the chord length of hub side.

4. as each blower-use impeller among the claim 1-3, it is characterized in that described each blade has the trailing edge (5) of the leading edge (4) of circular arc and the shape that comes to a point, be shaped as shape with progressive additive from described trailing edge to described leading edge.

5. as each blower-use impeller among the claim 1-3, it is characterized in that described each blade has the trailing edge (5) of the leading edge (4) of circular arc and the shape that comes to a point, the thickness from described trailing edge to described leading edge is to have roughly the same thickness.

6. as each blower-use impeller among the claim 1-3, it is characterized in that,

Described wheel hub is have circular cross-section trapezoidal,

When the least radius of the described circle of described wheel hub is the maximum radius of " r1 " and described wheel hub during for " r2 ", as represent hub radius be " r ", then is defined as r=(r1+r2)/2,

Distance from the center of described wheel hub to the maximum front end of described blade be " R2 ", and extremely the distance of the minimum front end of described blade is " R1 " from the center of described wheel hub, when the representative radius of impeller is " R " as described, then is defined as R=(R1+R2)/2,

When representing the mean square radius of gyration, be defined as Rr=((R for " Rr " ²+ r ²)/2) ^1/2,

Described " L " is the chord length of the described blade of the described representative mean square radius of gyration " Rr " position,

Described " b " is the length of the spanwise of the described blade of the position of the position that connects described representative hub radius " r " and described representative radius " R ".

7. as each blower-use impeller among the claim 1-3, it is characterized in that described impeller is used for the outdoor unit of air conditioner.

8. a gas fan comprises motor (12) and the impeller that is connected with described motor (1,15,16,40),

Described impeller comprises wheel hub (3) and is arranged at 2 pieces of blades (2) on this wheel hub,

It is that the center is symmetrical that each blade of described 2 pieces of blades is arranged to described wheel hub, when the chord length of the blade of the representative mean square radius of gyration " Rr " position of each blade of described 2 pieces of blades is the representative physical length of " L ", radial direction during for " b ",

The aspect ratio of described each blade " b/L " has the shape of " b/L≤1 " scope, it is characterized in that,

In the radial direction cross section of described each blade, be curve shape streamlined of spill (2a) from having with respect to the wind upside to the part of the most advanced and sophisticated side position of periphery near the position of the representative mean square radius of gyration of described blade,

From having with respect to the wind upside to the part of the position of hub side near the position of the representative mean square radius of gyration of described blade is the curve shape of convex (2b).

9. gas fan as claimed in claim 8 is characterized in that,

Described each blade has leg-of-mutton auxiliary blade (17),

1 leading edge at described blade of described auxiliary blade overlaps with the intersection point place of periphery, and 1 limit and the described leading edge of described auxiliary blade are close to formation.

10. gas fan as claimed in claim 8 is characterized in that,

The chord length of the outer circumferential side of described each blade is longer than the chord length of hub side.

11., it is characterized in that described impeller has the diagonal flow type structure as each described gas fan in the claim 8 to 10.

12., it is characterized in that described impeller has shaft flow structure as each described gas fan in the claim 8 to 10.

13. as each described gas fan in the claim 8 to 10, it is characterized in that,

Described wheel hub is have circular cross-section trapezoidal,

When the least radius of the described circle of described wheel hub is the maximum radius of " r1 " and described wheel hub during for " r2 ", as represent hub radius be " r ", then is defined as r=(r1+r2)/2,

Distance from the center of described wheel hub to the maximum front end of described blade be " R2 ", and extremely the distance of the minimum front end of described blade is " R1 " from the center of described wheel hub, and the representative radius of impeller is " R " as described, then is defined as R=(R1+R2)/2,

When representing the mean square radius of gyration, be defined as Rr=((R for " Rr " ²+ r ²)/2) ^1/2,

Described " L " is the chord length of the described blade of the described representative mean square radius of gyration " Rr " position,

Described " b " is the length of the spanwise of the described blade of the position of the position that connects described representative hub radius " r " and described representative radius " R ".

14., it is characterized in that described blower-use is in the outdoor unit of air conditioner as each described gas fan in the claim 8 to 10.

15. an air conditioner comprises indoor set (51), outdoor unit (52), is arranged on the pipe arrangement (53) between above-mentioned indoor set and the outdoor unit,

(a) described outdoor unit has heat exchanger (54) and gas fan (55),

(b) above-mentioned gas fan has motor (12) and the impeller that is connected with this motor (1,15,16,40),

(c) described impeller comprises wheel hub (3) and is arranged at 2 pieces of blades (2) on the described wheel hub,

Each blade of described 2 pieces of blades is that the center is arranged to symmetrically with described wheel hub,

The chord length of the blade of the representative mean square radius of gyration " Rr " position of each blade of described 2 pieces of blades is the representative physical length of " L " and radial direction during for " b ",

The aspect ratio of described each blade " b/L " has the shape of " b/L≤1 " scope, it is characterized in that, in the radial direction cross section of described each blade, from having with respect to the wind upside to the part of the most advanced and sophisticated side position of periphery near the position of the representative mean square radius of gyration of described blade is curve shape streamlined of spill (2a)

From having with respect to the wind upside to the part of the position of hub side near the position of the representative mean square radius of gyration of described blade is the curve shape of convex (2b).

16. air conditioner as claimed in claim 15 is characterized in that,

Described each blade has leg-of-mutton auxiliary blade (17),

1 leading edge at described blade of described auxiliary blade overlaps with the intersection point place of periphery, and 1 limit and the described leading edge of described auxiliary blade are close to formation.

17. air conditioner as claimed in claim 15 is characterized in that, the chord length of the outer circumferential side of described each blade is longer than the chord length of hub side.

18., it is characterized in that described gas fan has the diagonal flow type structure as each described air conditioner in the claim 15 to 17.

19., it is characterized in that described gas fan has shaft flow structure as each described air conditioner in the claim 15 to 17.

20. as each described air conditioner in the claim 15 to 17, it is characterized in that,

Described wheel hub is have circular cross-section trapezoidal,

When the least radius of the described circle of described wheel hub is the maximum radius of " r1 " and described wheel hub during for " r2 ", as represent hub radius be " r ", then is defined as r=(r1+r2)/2,

Distance from the center of described wheel hub to the maximum front end of described blade be " R2 ", and extremely the distance of the minimum front end of described blade is " R1 " from the center of described wheel hub, and the representative radius of impeller is " R " as described, then is defined as R=(R1+R2)/2,

When representing the mean square radius of gyration, be defined as Rr=((R for " Rr " ²+ r ²)/2) ^1/2,

Described " L " is the chord length of the described blade of the described representative mean square radius of gyration " Rr " position,

Described " b " is the length of the spanwise of the described blade of the position of the position that connects described representative hub radius " r " and described representative radius " R ".

Images