JP2002357197A - Impeller, blower, and refrigerator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent separation of an air flow, and restrict turbulence in a confluent flow in the condition of high air way resistance wherein speed increase of an axially discharged air flow from a pressure surface side trailing edge of a blade generates a large circulation vortex at a suction side leading part of the blade, separates an air flow along a negative pressure surface by a suction, turbulent air flow, enlarge turbulence when the pressure surface side air flow is confluent with the negative pressure surface side one at the trailing edge, deteriorate blowing performance of an impeller, and increase generated turbulence sound. SOLUTION: A recessed part (air flow direction changing means) 8b extended to be close to the trailing edge of the blade 8 at one end is provided on the side of a pressure surface 5 of the blade 8, and a protruded part 8a (air flow adhering means) is provided at a trailing edge part of the blade 8. An air flow of a large radial speed component passing the impeller 9 is converted into an axial direction by the recessed part 8b to increase air flow speed in the axial direction, and separation of the negative surface side air flow is restricted by the protruded part 8a. Turbulence when the air flow on the negative surface side is confluent with the air flow on the pressure surface side can thus be restricted, thereby deterioration of blowing performance of the impeller and increase of blowing noise can be restricted.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a blower used in refrigerators, air conditioners, office automation equipment, and the like.

[0002]

2. Description of the Related Art In recent years, axial blowers have been widely used in refrigerators, air conditioners, office automation equipment, and the like.
There is a tendency for smaller, higher-density, higher-performance, and lower-noise equipment.

A conventional axial blower is disclosed in Japanese Unexamined Patent Publication No.
What is shown in 44432 gazette is known.

Hereinafter, the above-described conventional axial blower will be described with reference to the drawings.

FIGS. 22 to 25 show a conventional axial-flow type impeller. FIG. 22 is a front view of the impeller, and FIG. 23 is xx of FIG.
24 is a cross-sectional view of the line, FIG. 24 is a front view of a main part showing the operation of the impeller,
FIG. 25 is a sectional view taken along line yy of FIG.

In FIGS. 22 and 23, reference numeral 1 denotes an impeller.
It comprises a hub 3 attached to the motor 2 and a plurality of blades 4 provided around the hub 3. Front edge 4a of feather 4
The protruding portion 6 protruding from the pressure surface 5 to the rear edge 4b is located on the outer peripheral side with a curvature. In FIG. 22, the leading edge 4a of the blade 4 is located closer to the drawing than the trailing edge 4b, and the impeller 1 has a structure in which air is blown to the back by rotating counterclockwise as indicated by the arrow.

The operation of the impeller configured as described above will be described below. First, the impeller 1 from the motor 2
When the blade rotates at a predetermined rotation speed, air flows into the impeller 1, and the static pressure and the dynamic pressure are added by the action of the blade 4, and the air is discharged out of the impeller 1 to perform a blowing action. By providing the protruding portion 6 on the pressure surface 5 side of the blade 4, the leakage flow from the pressure surface 5 to the suction surface 7 is first accelerated at the protruding start portion, and from the axial center side to the outer periphery of the blade along the pressure surface of the blade. By reducing the fluctuating flow component contained in the flowing main flow, the noise generation factor is reduced. That is, the pressure fluctuation at the outer peripheral end (the pressure difference between the pressure surface and the suction surface) is reduced by creating a leakage flow from the pressure surface to the suction surface, thereby suppressing an increase in noise.

[0008]

However, in the above configuration, when the impeller 1 is used under conditions of high airflow resistance, such as in a refrigerator, the airflow passing through the pressure surface 5 side of the blade 4 is reduced. As shown in FIG. 24, the airflow A has a strong radial component. The strong airflow having the radial component is applied to the pressure surface 5 of the blade 4.
It is blocked by the protrusion 6 provided on the side and converted in the axial direction, and is discharged from the trailing edge of the blade 4. Therefore, the pressure surface 5
From the trailing edge of the side increases. Further, under the condition of high wind path resistance, a large circulation vortex (not shown) is generated at the tip of the blade 4 on the suction side, so that the airflow sucked into the impeller 1 is disturbed and the airflow along the negative pressure surface 7 is increased. Causes peeling. That is, when the air flows on the pressure surface 5 side and the suction surface 7 side at the trailing edge merge, the speed difference becomes large, and the turbulence becomes large. Therefore, there is a problem that the air blowing performance of the impeller 1 is deteriorated and the generated turbulent noise increases.

The present invention relates to an impeller, a blower using the impeller, and a refrigerator using the blower, wherein an airflow having a large radial component passing through the impeller under a condition of high air path resistance is applied to a pressure surface side. The airflow direction converting means is converted in the axial direction by airflow direction converting means such as a concave portion provided on the blade, and a convex portion is provided on the trailing edge of the blade as airflow attaching means, and the chord length is partially increased. The airflow converted in the axial direction by the airflow near the airflow attaching means suppresses the separation of the airflow on the suction side and reduces the turbulence generated when the airflow on the pressure side and the airflow on the suction side at the trailing edge merge. It is an object of the present invention to suppress the deterioration of the air blowing performance of the impeller and to suppress the increase of the air blowing noise by suppressing.

[0010]

According to a first aspect of the present invention, there is provided an impeller comprising a hub mounted on a motor and a plurality of blades provided around the hub. Air flow direction changing means for converting the air flow sucked into the blade provided in the axial direction, and air flow attaching means for attaching a separation flow provided on the trailing edge of the blade, the air flow direction changing means The airflow converted in the axial direction by the airflow is characterized by flowing near the airflow adhering means, and under the condition where the impeller is installed and the configuration of the product airflow, the airflow resistance is high. In such cases, the airflow having a large radial velocity component passing through the impeller is converted in the axial direction by the airflow direction conversion means provided on the pressure surface side, and the axial airflow speed discharged from the pressure surface side increases,
Airflow attaching means is provided at the trailing edge of the blade, and the airflow converted in the axial direction by the airflow direction changing means flows near the airflow attaching means, thereby suppressing the separation of the airflow on the negative pressure side and being blown out from the negative pressure side. By suppressing the turbulence that occurs when the airflow and the airflow discharged from the pressure surface side merge, the deterioration of the blowing performance of the impeller is suppressed, and the increase of the blowing noise is suppressed.

The invention of the impeller according to claim 2 is the first invention.
In the invention described, the airflow direction changing means is a concave portion, the airflow attaching means is configured as a convex portion, and one end of the concave portion extends to near the trailing edge portion of the blade, In the condition where the impeller is installed and the configuration of the product air path, the air path resistance is high, so that the airflow with a large radial velocity component passing through the impeller is dammed by the recess provided on the pressure surface side. Stopped and converted in the axial direction, the airflow velocity in the axial direction discharged from the pressure surface side increases, and a convex portion is provided on the trailing edge of the blade, and the chord length is partially increased, so that the negative pressure surface By suppressing the separation of the airflow on the side, and suppressing the turbulence that occurs when the airflow blown from the negative pressure surface side and the airflow discharged from the pressure surface side merge, the deterioration of the air blowing performance of the impeller is suppressed, The effect of suppressing an increase in blast noise A.

[0012] The invention of the impeller according to claim 3 is based on claim 2.
In the invention described in (1), one end of the concave portion extends to the tip of the convex portion, and an airflow having a large radial velocity component passing through the impeller is blocked by the concave portion provided on the pressure surface side and the shaft is An axial airflow that is converted into a direction and discharged from the pressure surface side, and a convex portion is provided at the trailing edge of the blade, and the separation of the airflow on the negative pressure surface side is suppressed by partially increasing the chord length, By combining the airflow blown out from the negative pressure surface with the airflow at the same position, and suppressing the turbulence generated at the time of the merger, the effect of suppressing the deterioration of the airflow performance of the impeller and the increase of the airflow noise can be reduced. Have.

[0013] The invention of the blower according to claim 4 is the first invention.
In the impeller of the invention described in the above, the invention of the blower according to the fifth invention is the impeller of the second invention,
The blower according to the sixth aspect of the present invention is the impeller according to the third aspect of the present invention, wherein the configuration of the orifices each surrounding the outer periphery of the impeller is divided into a first side and a second side which partition the suction side and the discharge side. A mouth ring, an outer wall surrounding the outer circumference of the first and second plate-shaped mouth rings, and an opening facing the blade of the impeller between the first and second plate-shaped mouth rings. A swirling flow circulating space having a plurality of columns provided extending from the opening edges of the first and second plate-shaped mouth rings in a substantially radial direction of the impeller. A part of the airflow having a large radial velocity component passing through the impeller is sucked from the pressure surface side of the impeller into the swirling flow circulation space provided on the outer periphery of the impeller, and is rotated by the action of the blade in the swirl flow circulation space. The swirling flow turns in a strong rotating direction with a strong directional component. The swirl flow is prevented from being swirled by a plurality of pillars extending from the edge in a substantially radial direction of the impeller, and the swirl flow is discharged from the swirl flow circulation space to a low-pressure portion on the suction surface side of the blade, so that the suction surface side Since the speed of the airflow flowing along the air is increased, the turbulence generated when the airflow merges with the discharge airflow from the pressure surface side can be suppressed. Also, a part of the airflow passing through the impeller is sucked and exhausted in the swirling flow circulation space, and is discharged again to the discharge side, thereby suppressing the deterioration of the blowing performance of the impeller and suppressing the increase of the blowing noise. Having.

According to a seventh aspect of the present invention, there is provided a refrigerator according to the fourth aspect of the present invention, wherein the blower according to the fourth aspect is used in an air passage for supplying cooling air to a storage room in the refrigerator. By suppressing the deterioration, the cooling capacity is improved.

According to an eighth aspect of the present invention, there is provided a refrigerator according to the fourth aspect of the present invention, wherein the blower according to the fourth aspect of the present invention is used in an air passage for supplying air into a machine room of the refrigerator. The suppression has the effect of improving the condensation ability.

The invention of the refrigerator according to the ninth aspect provides the refrigerator according to the seventh or eighth aspect.
By using the blower of the described invention, by suppressing the deterioration of the blower performance as a blower, the effect that the cooling capacity is improved if used in the air path that supplies cooling air to the storage room in the refrigerator-freezer. In addition, when used in an air passage for supplying air into the machine room of a refrigerator-freezer, there is an effect that the condensation capacity is improved.

Further, a refrigerator according to a tenth aspect of the present invention uses the blower according to the sixth aspect of the present invention in the refrigerator according to the seventh or eighth aspect, wherein deterioration of the blowing performance as the blower is reduced. By suppressing it, it has the effect of improving the cooling capacity if it is used in the air passage that supplies cooling air to the storage room in the refrigerator, and also has the function of supplying air to the machine room of the refrigerator. When used, it has the effect of improving the condensation capacity.

[0018]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to FIGS.

The parts having the same configuration as the conventional one are denoted by the same reference numerals, and the description is omitted.

(Embodiment 1) FIGS. 1 to 15 show an impeller according to Embodiment 1 of the present invention. 1 and 2, reference numeral 8 denotes a plurality of blades provided around the hub 3, and a convex portion (air flow attaching means) 8a is provided at the rear edge of the blade 8, and a concave portion (air flow direction change). Means) 8b is blade 8
, And one end of the concave portion 8 b extends to near the rear edge of the blade 8. In FIG. 1, air has a structure in which air is blown to the back side by rotation in the direction indicated by the arrow.

With this configuration, when the impeller 9 is installed and the configuration of the product air path is such that the air path resistance is high as in a refrigerator, as shown in FIG. 8
The airflow B having a large velocity component in the radial direction passing therethrough is blocked by the concave portion 8b and converted in the axial direction (downward in the plane of FIG. 4). Therefore, the airflow velocity in the axial direction discharged from the pressure surface 5 side increases. In addition, as shown in FIG. 6, the airflow C that has conventionally separated on the negative pressure surface 7 side is provided with a convex portion 8a at the trailing edge of the blade 8 and partially increases the chord length, thereby increasing the length of the blade 8. Adhering like the airflow D near the trailing edge, separation of the airflow can be suppressed. Therefore, it is possible to suppress the turbulence generated when the airflow D blown out from the negative pressure surface 7 and the airflow E discharged from the pressure surface 5 merge, and to suppress the deterioration of the blowing performance of the impeller 9, An increase in noise can be suppressed.

Therefore, as shown in FIG. 8 by comparing the aerodynamic (P-Q) characteristics of the impeller of the present embodiment and the conventional impeller, the impeller of the present embodiment is It is possible to sufficiently suppress the decrease in the air volume under high static pressure conditions.

Here, in order to suppress the separation of the airflow, the blade 8
It is also conceivable to extend the entire trailing edge, but in that case, the weight of the entire impeller increases, and the load on the motor also increases, which causes a problem that the input increases, but as in the present invention, If the projection 8a is provided at a part of the trailing edge, separation of the airflow can be suppressed without increasing the weight of the impeller and increasing the load on the motor.

In this embodiment, the recess 8 is provided on the pressure surface 5 side.
However, as shown in FIG. 5, the same applies to the case where a convex portion 8d is provided on the negative pressure surface 7 side in accordance with the concave portion 8b provided on the pressure surface 5 side in order to make the thickness of the blade 8 uniform. The effect is obtained.

In the present embodiment, the shape of the convex portion 8a provided on the trailing edge of the blade 8 is substantially arc-shaped. However, as shown in FIGS. The same effect can be obtained by using a convex portion having a vertex of an arc shape and two substantially arc-shaped convex portions having a vertex.

In the present embodiment, the positions of the concave portion 8b provided on the pressure surface 5 side and the convex portion 8a provided on the trailing edge of the blade 8 are not limited, but as shown in FIG. Assuming that the distance between the outer peripheral end and the outer peripheral end of the blade 8 is DZ, as shown in FIG. 13, when the center position DM of the convex portion 8a is from around 0.5 DZ to near the outer periphery 0.9Z, near the outer periphery of the blade 8 Due to the large rotational energy, the airflow velocity in the axial direction converted by the concave portion 8b also increases, and the peripheral speed of the blade 8 near the outer periphery is also high, so that the airflow D adhering near the trailing edge due to the convex portion 8a of the blade 8 By increasing the speed, a greater effect can be obtained.

In the present embodiment, the size of the projection 8a provided on the trailing edge of the blade 8 is not limited, but as shown in FIG. .
A great effect can be obtained in the range around 9DZ. In addition, as shown in FIG.
A great effect can be obtained in the range from around 2DZ to around DZ. Further, for example, when the position DM of the center of the convex portion 8a is from about 0.7 DZ to about 0.8 DZ,
The height H of the projection 8a is in the range of about 0.1 to 0.35 in the range where the base DT of
It has been confirmed that the effect is the greatest when it is near. When the position DM of the center of the convex portion 8a is in another range,
A similar effect can be obtained if the design is made taking into account the length DT of the base of the projection 8a and the height H of the projection 8a as appropriate.

(Embodiment 2) FIG. 16 shows an impeller according to Embodiment 2 of the present invention. The same components as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.

FIG. 16 is characterized in that one end of the concave portion 8b provided on the blade 8 extends to the tip of the convex portion 8a provided on the blade 8.

With this configuration, the airflow F having a large radial velocity component passing through the impeller 9 is blocked by the concave portion 8b provided on the pressure surface 5 side, converted into an axial direction, and discharged in the axial direction from the pressure surface 5 side. Airflow, and the protruding portion 8
a, the separation of the airflow D on the suction surface 7 side is suppressed by partially increasing the chord length, and the airflow blown out from the suction surface 7 side is merged at the same position, which is generated at the time of the merger. By suppressing the turbulence, the deterioration of the blowing performance of the impeller 9 can be suppressed, and the increase in the blowing noise can be suppressed.

(Third Embodiment) FIGS. 17 to 20 show a blower according to a third embodiment of the present invention. The same components as those in the first and second embodiments are denoted by the same reference numerals, and description thereof is omitted.

17 and 18, reference numeral 16 denotes an entire blower, and reference numeral 12 denotes an outer wall. Two plate-shaped mouth rings for partitioning the suction side and the discharge side on the outer periphery of the blade 8, a first mouth ring 10, The outer periphery of the second mouth ring 11 is surrounded. Reference numeral 14 denotes a swirling flow circulation space, which has an opening 13 facing the blade 8 between the first mouth ring 10 and the second mouth ring 11. Reference numerals 15a and 15b denote a plurality of columns provided in the swirling flow circulation space, and the blades 8 extend from the opening edges of the first mouth ring 10 and the second mouth ring 11.
Are provided to extend substantially in the radial direction.

With this configuration, when the blower 16 is installed and the configuration of the product air path is such that the air path resistance is high as in a refrigerator, as shown in FIG. A portion of the airflow G having a large radial velocity component passing through the opening 13 flows into the swirling flow circulation space 14 through the opening 13.

Here, as shown in FIG. 19, first, immediately after the blade 8 has passed through one pillar 15a, the blade 8 of the pillar 15a
The airflow H is on the side away from the
b, the airflow I near the middle in the circumferential direction, and the airflow J near the blade 8 of the next column 15b, where the blade 8 approaches, the blade 8
Flows into the swirling flow circulating space 14 from the pressure surface 5 side. At this time, the rotating blade 8 turns into a swirling flow flowing in the circumferential direction of the blade 8 and flows in the swirling flow circulation space 14.

Then, as shown in FIG. 20, when the blade 8 moves in the rotation direction and passes through the next column 15b, the airflow H,
Both I and J are prevented from turning by the column 15b, the flow direction is deflected in the direction of the blade 8, and is discharged again from the negative pressure surface 7 side of the blade 8 to the blade 8 side.

As described above, by discharging from the swirling flow circulation space 14 to the low pressure portion of the blade 8 on the side of the negative pressure surface 7,
In order to increase the speed of the airflow flowing along the negative pressure surface 7 side,
Turbulence generated at the time of merging with the discharge airflow from the pressure surface 5 side can be more effectively suppressed. In addition, a part of the airflow passing through the impeller is sucked and exhausted in the swirling flow circulation space 14 and discharged again to the discharge side, thereby suppressing the deterioration of the blowing performance of the impeller and suppressing the increase of the blowing noise. Can be.

(Embodiment 4) FIG. 21 shows a refrigerator-freezer according to Embodiment 4 of the present invention. The same components as those in the first to third embodiments are denoted by the same reference numerals, and description thereof is omitted.

In FIG. 21, reference numeral 150 denotes the entire refrigerator-freezer, and 101 denotes a storage room. The air sucked from the air suction port 102 of the storage room by the blower 16 passes through the air passage and exchanges heat with the evaporator 103 to discharge air from the storage room. The air discharged from the outlet 104 and supplied to the storage room 101 is cooled. The blower 16 is used in an air passage for supplying cooling air to the storage room 101 in the refrigerator. In the present embodiment, these are configured in an upper stage and a lower stage, respectively.

Reference numeral 105 denotes a machine room in which the compressor 10
6, the evaporating dish 107 and the condenser 108.
The air sucked from the air suction port 109 of the machine room by the blower 16a passes through the air path and exchanges heat with the condenser 108 and is discharged from the air discharge port 110 of the machine room. The blower 16a is used in an air passage that supplies air into the machine room 105 of the refrigerator.

With this configuration, the blowers 16, 16a can be operated under the condition that the air passage resistance is high, such as the refrigerator 150.
As a result, it is possible to suppress the deterioration of the blowing performance.

Accordingly, since the amount of air passing through the evaporator 103 increases, the efficiency of heat exchange is improved, and the cooling capacity of the refrigerator 150 is improved. Further, since the amount of air passing through the condenser 108 and the compressor 106 increases, the compressor 106 can be cooled, the heat exchange efficiency of the condenser 108 is improved, and the condensing ability of the refrigerator 150 is improved.

[0042]

As described above, the invention according to claim 1 includes a hub attached to a motor and a plurality of blades provided around the hub, and is provided on a pressure surface side of the blade. Airflow direction changing means for converting the airflow sucked into the blade in the axial direction, and airflow attaching means for attaching a separation flow provided on the trailing edge of the blade, the airflow direction converting means having an axial direction. It is characterized in that the airflow converted to flows near the airflow attaching means, such as in the state where the impeller is installed or the configuration of the product airflow path, when the airflow resistance becomes high, The airflow having a large radial velocity component passing through the impeller is converted in the axial direction by the airflow direction conversion means provided on the pressure surface side, and the axial airflow velocity discharged from the pressure surface side increases, and the trailing edge of the blade Air flow attachment means Since the airflow converted in the axial direction by the airflow direction conversion means flows near the airflow attaching means, the separation of the airflow on the suction side is suppressed, and the airflow blown out from the suction side and the airflow discharged from the pressure side By suppressing the turbulence generated at the time of merging with the impeller, the effect of suppressing the deterioration of the air blowing performance of the impeller and suppressing the increase of the air blowing noise can be obtained.

According to a second aspect of the present invention, in addition to the first aspect of the present invention, the airflow direction changing means is a recess,
The airflow adhering means is a convex portion, and one end of the concave portion extends to near the trailing edge of the blade. In the case where the road resistance is high, the airflow having a large radial velocity component passing through the impeller is blocked by the concave portion provided on the pressure surface side, converted into an axial direction, and discharged in the axial direction from the pressure surface side. As the airflow velocity increases, a convex portion is provided at the trailing edge of the blade to partially suppress the separation of the airflow on the suction side by increasing the chord length, and the airflow blown out from the suction side By suppressing the turbulence generated at the time of merging with the airflow discharged from the pressure surface side, it is possible to obtain the effect of suppressing the deterioration of the blowing performance of the impeller and the increase of the blowing noise.

According to a third aspect of the present invention, in addition to the second aspect of the invention, since one end of the concave portion extends to the tip of the convex portion, a radial velocity component passing through the impeller is large. The airflow is blocked by the concave portion provided on the pressure surface side and is converted in the axial direction, and the airflow in the axial direction discharged from the pressure surface side, and a convex portion is provided on the trailing edge of the blade, and the chord length is partially set. By increasing the length, the separation of the airflow on the suction side is suppressed, the airflow blown out from the suction side is merged at the same position, and the turbulence generated at the time of the merger is further suppressed. The effect of suppressing deterioration and suppressing an increase in blowing noise can be obtained.

The invention of claim 4 is in addition to the invention of claim 1, the invention of claim 5 is in addition to the invention of claim 2, and the invention of claim 6 is in addition to the invention of claim 2. Item 3. In addition to the invention described in Item 3, the configuration of the orifice surrounding the outer periphery of the blade is defined by first and second plate-shaped mouth rings that partition a suction side and a discharge side, and the first and second plate-shaped mouth rings. An outer wall surrounding the outer periphery of the mouth ring, and a swirling flow circulation space having an opening facing the blade of the impeller between the first and second plate-shaped mouth rings; By providing a blower using the impeller of the present invention, wherein there are a plurality of columns provided extending from the opening edge of the plate-shaped mouth ring substantially in the radial direction of the impeller, the radius passing through the impeller Part of the airflow having a large directional velocity component flows from the pressure surface side of the blade to the outer periphery of the impeller. The swirling flow is sucked into the swirling flow circulation space, and becomes a swirling flow in which the circumferential component is swirled in a strong rotational direction by the action of the blade in the swirling flow circulation space, but extends from the opening edge in a substantially radial direction of the impeller. The swirling of the swirling flow is prevented by the plurality of columns provided, and the speed of the airflow flowing along the suction surface side is increased by discharging from the swirling flow circulation space to the low pressure portion on the suction surface side of the blade. Therefore, it is possible to suppress the turbulence generated at the time of merging with the discharge airflow from the pressure surface side. In addition, a part of the airflow passing through the impeller is sucked and exhausted in the swirling flow circulation space and discharged again to the discharge side, thereby suppressing deterioration of the airflow performance of the impeller and suppressing an increase in airflow noise. Is obtained.

Further, according to the present invention, the use of the refrigerator of the present invention in the air passage for supplying the cooling air to the storage room in the refrigerator has the effect of deteriorating the blowing performance of the fan. Therefore, the effect of improving the cooling capacity can be obtained.

According to the eighth aspect of the present invention, deterioration of aerodynamic performance as a blower is suppressed by providing a refrigerator using the blower of the present invention in an air passage for supplying air into a machine room of the refrigerator. Therefore, an effect that the condensation ability is improved can be obtained.

Further, the invention according to claim 9 and the invention according to claim 10 are used in an air passage for supplying cooling air to a storage room in a freezer-refrigerator by suppressing deterioration of air blowing performance as a blower. If it is used in an air passage that supplies air into the machine room of a refrigerator-freezer, it has the effect of improving the condensation capacity.

[Brief description of the drawings]

FIG. 1 is a front view of an impeller according to Embodiment 1 of the present invention.

FIG. 2 is a sectional view taken along line aa of FIG. 1;

FIG. 3 is an essential part front view showing the operation of the impeller according to the first embodiment of the present invention.

FIG. 4 is a sectional view taken along line bb of FIG. 3, showing the operation of the impeller according to the first embodiment of the present invention.

FIG. 5 is a sectional view taken along the line bb of FIG. 3, showing another operation of the impeller according to the first embodiment of the present invention.

FIG. 6 shows the operation of the impeller in the conventional example,
-C sectional view

FIG. 7 is a sectional view taken along line dd of FIG. 3, showing the operation of the impeller according to the first embodiment of the present invention.

FIG. 8 is a characteristic diagram showing a comparison of aerodynamic (PQ) characteristics of the blower according to the first embodiment of the present invention and a conventional impeller.

FIG. 9 is a front view of a main part of another impeller according to the first embodiment of the present invention.

FIG. 10 is a front view of a main part of another impeller according to the first embodiment of the present invention.

FIG. 11 is a front view of a main part of another impeller according to the first embodiment of the present invention.

FIG. 12 is a front view of a main part of the impeller according to the first embodiment of the present invention.

FIG. 13 is a characteristic diagram showing a relationship between the position DM of the center of the convex portion and the static pressure P at the operating point in the first embodiment of the present invention.

FIG. 14 is a characteristic diagram showing the relationship between the length DT of the base of the protrusion and the static pressure P at the operating point in the first embodiment of the present invention.

FIG. 15 shows a height H of the convex portion according to the first embodiment of the present invention.
Graph showing the relationship between the static pressure P at the operating point and the operating point

FIG. 16 is an essential part front view showing the operation of the impeller according to the second embodiment of the present invention.

FIG. 17 is a front view of a blower according to Embodiment 3 of the present invention.

18 is a sectional view taken along line ee in FIG. 17;

FIG. 19 is a sectional view taken along the line ff of FIG. 18 showing the operation of the blower according to the third embodiment of the present invention.

FIG. 20 is a cross-sectional view in which the blades of FIG. 19 have moved in the rotation direction.

FIG. 21 is a side longitudinal sectional view of a refrigerator-freezer according to a fourth embodiment of the present invention.

FIG. 22 is a front view of an impeller in a conventional example.

FIG. 23 is a sectional view taken along line xx of FIG. 22;

FIG. 24 is a front view of a main part showing the operation of an impeller in a conventional example.

FIG. 25 is a sectional view taken along line yy of FIG. 24;

[Explanation of symbols]

 Reference Signs List 2 Motor 3 Hub 5 Pressure surface 8 Blade 8a Convex part (air flow attaching means) 8b Recess (air flow direction changing means) 9 Impeller 10 First mouth ring 11 Second mouth ring 12 Outer wall 13 Opening 14 Swirling flow circulation space 15a, 15b Pillar 16, 16a Blower 101 Storage room 105 Machine room 150 Refrigerator

Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat II (Reference) F25D 17/06 304 F25D 17/06 304 (72) Inventor Takumi Kida 4-5-2-5 Takaida Hondori, Higashi Osaka City, Osaka Prefecture No. Matsushita Refrigeration Co., Ltd. F-term (reference) 3H033 AA02 AA18 BB02 BB08 BB20 CC01 CC03 DD03 DD12 DD17 EE06 EE08 EE19 3H034 AA02 AA18 BB02 BB08 BB20 CC01 CC03 DD05 DD12 EE06 EE08 EE12 EE18 3H035 CC01 DD01

Claims (10)

[Claims] 1. A hub mounted on a motor, and a plurality of blades provided around the hub, wherein an airflow sucked into the blade provided on a pressure surface side of the blade is converted in an axial direction. Airflow direction changing means, and airflow attaching means for attaching a separated flow provided at the trailing edge of the blade, wherein the airflow converted in the axial direction by the airflow direction changing means flows near the airflow attaching means. An impeller characterized in that: 2. The impeller according to claim 1, wherein the airflow direction changing means is formed as a concave portion, and the airflow attaching means is formed as a convex portion, and one end of the concave portion extends to near the trailing edge of the blade. . 3. The impeller according to claim 2, wherein one end of the concave portion extends to a tip of the convex portion. 4. A hub attached to a motor, and a plurality of blades provided around the hub, wherein an airflow sucked into the blade provided on a pressure surface side of the blade is converted in an axial direction. Airflow direction changing means, and airflow attaching means for attaching a separated flow provided at the trailing edge of the blade, wherein the airflow converted in the axial direction by the airflow direction changing means flows near the airflow attaching means. An impeller, an orifice surrounding the outer periphery of the impeller, a first and a second plate-shaped mouth ring for dividing a suction side and a discharge side, and the first and the second plate-shaped mouth rings. An outer wall surrounding the outer periphery of the mouth ring, and a swirling flow circulating space having an opening facing the blade of the impeller between the first and second plate-shaped mouth rings; From the opening edge of the plate-shaped mouth ring of the impeller A blower characterized by having a plurality of columns extending substantially in the radial direction. 5. An airflow direction changing means provided on a blade of an impeller is formed as a concave portion, and an airflow attaching means is formed as a convex portion, and one end of the concave portion extends to near a trailing edge portion of the blade. The blower according to claim 4, wherein 6. The blower according to claim 5, wherein one end of the concave portion of the airflow direction changing means provided on the blade of the impeller extends to the tip of the convex portion. 7. A hub mounted on a motor, and a plurality of blades provided around the hub, and converts an airflow sucked into the blades provided on a pressure surface side of the blades in an axial direction. Airflow direction changing means, and airflow attaching means for attaching a separated flow provided at the trailing edge of the blade, wherein the airflow converted in the axial direction by the airflow direction changing means flows near the airflow attaching means. An impeller, an orifice surrounding the outer periphery of the impeller, a first and a second plate-shaped mouth ring for dividing a suction side and a discharge side, and the first and the second plate-shaped mouth rings. An outer wall surrounding the outer periphery of the mouth ring, and a swirling flow circulating space having an opening facing the blade of the impeller between the first and second plate-shaped mouth rings; From the opening edge of the plate-shaped mouth ring of the impeller A refrigerator comprising a plurality of pillars extending substantially in the radial direction, wherein the blower is used in an air passage for supplying cooling air to a storage room in the refrigerator. 8. A hub mounted on a motor, and a plurality of blades provided around the hub, wherein an airflow sucked into the blades provided on a pressure surface side of the blades is converted in an axial direction. Airflow direction changing means, and airflow attaching means for attaching a separated flow provided at the trailing edge of the blade, wherein the airflow converted in the axial direction by the airflow direction changing means flows near the airflow attaching means. An impeller, an orifice surrounding the outer periphery of the impeller, a first and a second plate-shaped mouth ring for dividing a suction side and a discharge side, and the first and the second plate-shaped mouth rings. An outer wall surrounding the outer periphery of the mouth ring, and a swirling flow circulating space having an opening facing the blade of the impeller between the first and second plate-shaped mouth rings; From the opening edge of the plate-shaped mouth ring of the impeller A refrigerator comprising a plurality of pillars extending substantially in the radial direction of the refrigerator, wherein the blower is used in an air passage for supplying air into a machine room of the refrigerator. 9. An airflow direction changing means provided on a blade of an impeller is formed as a concave portion, and an airflow attaching means is formed as a convex portion, and one end of the concave portion extends to near a trailing edge portion of the blade. The refrigerator-freezer according to claim 7 or 8, wherein 10. The refrigerator according to claim 7, wherein one end of the concave portion of the airflow direction changing means provided on the blade of the impeller extends to the tip of the convex portion.