JP2006144764A - Impeller structure for axial flow type heat radiating fan - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide impeller structure for an axial flow type heat radiating fan capable of relatively increasing blowing capacity of the impeller and capable of reducing blowing noise. <P>SOLUTION: A plurality of blades are arranged with inclination to be symmetry in the periphery of a hub. In the vertical direction in parallel with a rotary shaft center 40, each of adjacent two blades 42 are overlapped with each other at an appropriate ratio in the vertical direction to form a first vertical overlap zone A1 and a second vertical overlap zone A2 in each of the blades. The first and the second vertical overlap zones A1 and A2 are formed not to reach the radial peripheral edge of the blade. Consequently, in the vertical direction in parallel with the rotary shaft center, a front edge of any blades of the impeller is formed with the only local overlap with a rear edge of the adjacent blade at an appropriate ratio, and furthermore, the overlap zone in the vertical direction is formed not to reach the radial outside edge of the blade. With this structure, the blowing noise due to excessive overlap can be relatively reduced, and blowing quantity of the impeller can be relatively increased, and while the blowing noise can be reduced. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an impeller structure for an axial-flow-type heat dissipation fan, and in particular, two adjacent blades of a hub are formed with an overlapping zone in an appropriate proportion in the vertical direction. By being formed so as not to reach the outer edge in the direction, the present invention relates to an impeller structure that can increase the amount of wind entering and reduce the noise of air blowing.

  As shown in FIG. 6, the conventional impeller structure of the axial flow type heat radiating fan includes a hub 101 and a plurality of blades 102, and the impeller 10 applied to the axial flow type heat radiating fan. Is housed inside the shell seat 20. A plurality of blades 102 are provided so as to be inclined around the outer periphery of the hub 101 so that the airflow can be driven to flow in the axial direction.

Further, as shown in FIGS. 7 and 8, the conventional impeller structure of the axial-flow-type heat radiating fan includes a rotating shaft 30, an assembly hub 31, and a plurality of assembly blades 32. The assembly hub 31 is composed of an upper hub 31a and a lower hub 31b. The upper hub 31a is provided with a plurality of upper blades 32a, and the lower hub 31b is provided with a plurality of lower blades 32b. The upper blade 32a and the lower blade 32b are aligned and connected to form the assembly blade 32. According to the assembly method described above, any assembly blade 32 is formed so as to overlap the adjacent assembly blade 32 in the longitudinal direction parallel to the rotation axis 30. As shown in FIG. 8, the front edge 321 of each assembly blade 32 is formed so as to completely cover the rear edge 322 of the adjacent assembly blade 32 (for example, Patent Document 1, 2 and 3).
Republic of China Notification No. 413273 Republic of China Notification No. 553324 Republic of China Notification No. 570493

  In the impeller structure of the conventional axial flow type heat radiating fan as described above, the adjacent blades 102 are overlapped with each other in the vertical direction parallel to the rotation axis because the impeller 10 is normally cut after being molded. Can only be designed to not. Furthermore, in the fluid dynamics, the total blown amount of the impeller 10 is directly proportional to the total amount of the blades 102 or the total blown area. In other words, the impeller 10 can not only relatively increase the total amount of the blades 102 or the total air blowing area without first overcoming the above-described limitation of die cutting after molding. There was a problem that the amount of blast could not be increased.

  Moreover, in the conventional impeller structure of an axial-flow-type heat radiation fan as described above, the total ventilation area and the total amount of the assembly blades 32 can be increased by the above-described overlapping arrangement method. However, since the impeller 3 is not designed with a perfect superposition arrangement, the total blown amount can be greatly increased. However, since the noise increases as a large amount of blown air is generated, there is an actual use effect. There was a problem of lowering. Thus, it is necessary to further improve the conventional impeller structure of the axial flow type heat dissipating fan.

  The present invention has been invented in view of such problems, and the object of the present invention is to make the front edge of any blade of an impeller a vertical parallel to the rotational axis from the rear edge of an adjacent blade. Only the local overlap in the vertical direction is formed in an appropriate proportion in the direction, and the overlap zone in the vertical direction is formed so as not to reach the outer edge in the radial direction of the blade, thereby relatively reducing the noise of the air blow due to excessive superposition. Therefore, it is an object of the present invention to provide an impeller structure for an axial-flow heat dissipating fan that can relatively increase the amount of air blown by the impeller and reduce the noise of the air blow.

  The first object of the present invention is that each adjacent two blades of the hub have a vertical overlap zone formed in an appropriate proportion in the longitudinal direction parallel to the rotation axis, and the vertical overlap zone is the diameter of the blade. Since it is formed so as not to reach the outer edge in the direction, it is intended to provide an impeller structure of an axial flow type heat radiating fan that can increase the amount of air flow and reduce the noise of the air flow.

In order to achieve the above object, the impeller structure of the axial flow type heat dissipating fan according to the present invention is as follows. That is,
It is composed of a hub and a plurality of blades. The hub is provided at the center position of the inner surface so that the rotation axis projects. The plurality of blades are arranged in a slanting manner so as to be symmetrical around the outer periphery of the hub, and each blade has a front edge, a rear edge, a radial inner edge, and a radial outer edge, and is arranged in a vertical direction parallel to the rotation axis. By forming the two adjacent blades in the direction so as to overlap in the vertical direction in an appropriate proportion, a first vertical overlap zone and a second vertical overlap zone are formed in each blade. The first longitudinal overlap zone is formed so as to extend outward from the front edge and the radially inner edge, but is formed so as not to reach the radially outer edge of the blade, and the second longitudinal overlap zone is formed with the rear edge. Although it is formed so as to extend outward from the radially inner edge, it is formed so as not to reach the radially outer edge of the blade, so that the amount of wind entering is relatively increased by the impeller and at the same time, the noise of the air blow is reduced. Can be reduced.

  In the impeller structure of the axial flow type heat dissipation fan according to the present invention, the rear edge of the blade is projected on the adjacent blade in the vertical direction to form a rear edge projection line, and the first vertical overlap zone is the front edge, It can also be formed between the radially inner edge and the rear edge projection line. Also, the front edge and the radially inner edge meet to form a front base point, the rear edge projection line intersects with the front edge to form a first overlap point, and the length from the front base point to the first overlap point is It can also be 1/5 to 4/5 of the actual total length of the front edge. Also, the front edge and the radial inner edge intersect to form a front base point, and the rear edge projection line intersects the radial inner edge to form a second overlap point, and the length from the front base point to the second overlap point Can also be 1/6 to 5/6 of the actual total length of the radially inner edge. Also, the front edge of the blade is projected on the adjacent blade in the vertical direction to form a front edge projection line, and the second vertical overlap zone is formed between the rear edge, the radial inner edge and the front edge projection line. You can also. Also, the rear edge and the radially inner edge meet to form the rear base point, the front edge projection line intersects with the rear edge to form the third overlap point, and the rear overlap point to the third overlap point Can also be 1/5 to 4/5 of the actual total length of the rear edge. Also, the rear edge and the radially inner edge meet to form the rear base point, the front edge projection line intersects the radial inner edge to form the fourth overlap point, and the length from the front base point to the fourth overlap point It can also be from 1/6 to 5/6 of the actual total length of the radially inner edge. Further, in the longitudinal direction parallel to the rotation axis, the front edge and the rear edge of each adjacent two blades overlap in the longitudinal direction to form an angle, and the angle is interposed between 10 ° and 90 °. It can also be formed. In addition, the front end of the front edge of each blade and the rear end of the rear edge are connected to form a straight line relative to the radial plane of the hub, and an inclination angle is formed between the straight line and the radial plane. In addition, the inclination angle may be formed to be between 10 ° and 70 °.

  According to the impeller structure of the axial heat radiating fan of the present invention, two adjacent blades of the hub are formed with a vertical overlapping zone in an appropriate proportion in the vertical direction parallel to the rotation axis, and the vertical direction. Since the overlap zone is formed so as not to reach the outer edge in the radial direction of the blade, there is an advantage that the amount of blowing air can be increased and the noise of blowing can be reduced.

  Embodiments of the present invention will be described below with reference to the drawings.

  1 and 2, the impeller 4 according to the embodiment of the present invention is provided with a rotation axis 40 (not shown, see FIG. 3), a hub 4 and a plurality of blades. The rotation axis 40 is provided so as to protrude in the center of the inner surface of the hub 41, and the rotation axis 40 is used for coupling with the motor 6. The blades 42 are inclined and arranged so as to be appropriately symmetric around the outer periphery of the hub 41. The blade 42 is formed with a front edge 421, a rear edge 422, a radial inner edge 423, and a radial outer edge 424. The front edge 421, the rear edge 422, the radial inner edge 423, and the radial outer edge 424 are respectively in accordance with the order. Are formed on the wind entry side, the wind discharge side, the side connected to the outer periphery of the hub 41, and the other side far from the hub 41. The front edge 421, the rear edge 422, the radial inner edge 423, and the radial outer edge 424 can be formed in either a straight shape or a curved shape having an appropriate curvature depending on the demand of the product. Further, the front edge 421 and the radial inner edge 423 intersect to form a front base point I1, and the front edge 421 and the radial outer edge 424 intersect to form a front end point I2. Further, the rear edge 422 and the radial inner edge 423 intersect to form a rear base point O1, and the rear edge 422 and the radial outer edge 424 intersect to form a rear end point O2.

Referring again to FIGS. 1 and 2, in the longitudinal direction parallel to the rotational axis 40, the rear edge 422 defined by projecting the rear edge 422 of any blade 42 onto the other blade 42 adjacent in the longitudinal direction. A projection line L1 is formed. The rear edge projection line L1 intersects with the front edge 421 to form a first overlap point P1, and the rear edge projection line L1 intersects with the radial inner edge 423 to form a second overlap point P2. Thereby, the rear side edge projection line L1, the front side edge 421, and the radial inner edge 423 are formed by defining the first vertical overlapping zone A1 together. The length from the front base point I1 to the first overlapping point P1 is preferably interposed between 1/5 and 4/5 of the actual total length of the front edge 421, and is particularly ½. That is, length D _(I1 - _P1) = 1 / _5-5 / 5 × length D _(I1-I2) . Further, the length from the front base point I1 to the second overlapping point P2 is preferably interposed between 1/6 and 5/6 of the actual total length of the radial inner edge 423, and is particularly ½. That is, length D _(I1 - _P2) = 1 / 6-5 / 6 × length D _(I1-O1) .

1 and 2 again, in the longitudinal direction parallel to the rotation axis 40, the front edge 421 of any blade 42 is projected on the other blade 42 adjacent in the longitudinal direction so that the front edge projection line L2 is It is formed. The front edge projection line L2 intersects with the rear edge 422 to form a third overlap point P3, and the front edge projection line L2 intersects with the radial inner edge 423 to form a fourth overlap point P4. Accordingly, the front edge projection line L2, the rear edge 422, and the radial inner edge 423 are formed by defining the second vertical overlap zone A2. The length from the front base point O1 to the third overlapping point P3 is preferably interposed between 1/5 and 4/5 of the actual total length of the rear edge 422, and is particularly 1/2. That is, length D _(O1 - _P3) = 1 / _5-5 / 5 × length D _(O1-O2) . Furthermore, the length from the rear base point O1 to the fourth overlapping point P4 is preferably interposed between 1/6 and 5/6 of the actual total length of the radial inner edge 423, and is particularly ½. That is, length D _(O1 - _P4) = 1 / 6-5 / 6 × length D _(O1-I1) .

  3 and 4, in the longitudinal direction parallel to the rotation axis 40, the front edge 421 and the rear edge 422 of each adjacent two blades 42 overlap in the longitudinal direction to form an angle θ1. θ1 is preferably interposed between 10 ° and 90 °, in particular 45 °. In addition, each of the two adjacent blades 42 is formed so that the angle when the rear edge projection line L1 and the front edge projection line L2 intersect has the same angle θ1. Further, even when the first vertical overlap zone A1 and the second vertical overlap zone A2 are overlapped at the maximum, the first vertical overlap zone A1 and the second vertical overlap zone A2 are formed so as not to reach (or extend) the radial outer edge 422 of the blade 42. Further, the front end point I2 of the front edge 421 of each blade 42 and the rear end point O2 of the rear edge 422 are connected to the radial plane P of the hub 41 to form a straight line L, and the straight line L and the radial plane are connected. An inclination angle θ2 is formed between P and the inclination angle θ2, which is preferably between 10 ° and 70 °, in particular 30 °.

  Referring again to FIG. 1, the shell seat 5 according to the embodiment of the present invention is provided with an air flow passage 50, a wind inlet 51, a wind outlet 52, a base 53, and a plurality of flow guide members 54. The base 53 is positioned on the wind outlet 52 side, and is supported and connected to the inner peripheral wall of the airflow passage 50 by the flow guide support member 54. The base 53 is used to mount the motor 6 so that the impeller 4 can be coupled and the impeller 4 can be driven. Furthermore, by forming the flow guide support member 54 so as to have an appropriate inclination corresponding to the blowing direction of the blades 42 of the impeller 4, it is possible to provide the effects of the flow guide and the pressure increase.

  2 and 5, the impeller 4 according to the embodiment of the present invention is assembled with the shell seat 5 to form an axial flow type heat radiation fan. During operation, the impeller 4 rotates to drive the airflow, so that the airflow enters the airflow passage 50 from the wind advance inlet 51, and then further increases the pressure through the flow guide support member 54, and finally the wind discharge port again. Exported after 52.

  As described above, according to the impeller structure of the axial flow type heat radiating fan of the present invention, any blade 42 of the impeller 4 is different from the two adjacent blades 42 in the front-rear direction, respectively, in the first vertical overlap zone A1 and the second. A vertical overlap zone A2 is formed. In particular, the first vertical overlap zone A1 and the second vertical overlap zone A2 are formed so as not to reach the radial outer edge 422 of the blade 42. Thereby, compared with the conventional impeller 1 shown in FIG. 6, the impeller 4 of the present invention can surely increase the total arrangement quantity and the total blowing area of the vanes 42, so that the total blowing quantity can be further increased. it can. Furthermore, compared with the conventional assembly type impeller 3 shown in FIG. 7, according to the impeller 4 of the present invention, it is possible to reduce the overlapping of the zones close to the radial outer edge 424 of the blades 42. Therefore, it is possible to relatively reduce the occurrence of blowing noise due to excessive superposition. Thus, according to the design of the impeller 4 of the present invention, it is possible to relatively increase the amount of air blown by the impeller and reduce the noise of the air blow.

  The present invention may be implemented in other ways without departing from the spirit and essential characteristics thereof. Accordingly, the preferred embodiments described herein are illustrative and not limiting.

It is a disassembled perspective view which shows the impeller structure of the axial flow type thermal radiation fan of the Example of this invention. It is a local enlarged view of the impeller structure of FIG. It is a top view which shows the impeller structure of the axial flow type thermal radiation fan of the Example of this invention. It is a side view which shows the impeller structure of the axial flow type thermal radiation fan of the Example of this invention. It is a partial notch perspective view which shows the assembled state by the impeller structure of the axial-flow-type heat radiating fan of the Example of this invention. It is sectional drawing which shows the state assembled by the impeller structure of the conventional axial flow type thermal radiation fan. It is sectional drawing which shows the assembled state by the impeller structure of another conventional axial flow type heat radiation fan. It is a top view which shows the impeller structure of the axial flow type thermal radiation fan of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Impeller 101 Hub 102 Blade 20 Shell 3 Impeller 30 Rotation shaft center 31 Assembly hub 31a Upper hub 31b Lower hub 32 Assembly blade 321 Front edge 322 Rear edge 4 Impeller 40 Rotation center 41 Hub 42 Blade 421 Front edge 422 Rear edge 423 Radial inner edge 424 Radial outer edge 5 Shell seat 50 Airflow passage 51 Wind advance inlet 52 Wind outlet 53 Base seat 54 Current guide member 6 Motor A1 First vertical overlap zone A2 Second vertical overlap zone I1 Front base point I2 Front end point L1 Rear edge projection line L2 Rear projection line L Straight line O1 Rear base point O2 Rear end point P Radial plane P1 First overlap point P2 Second overlap point P3 Third overlap point P4 Fourth Superposition point θ1 angle θ2 tilt angle

Claims (9)

  It is an impeller (4) structure of an axial-flow-type heat dissipating fan composed of a hub (41) and a plurality of blades (42). The hub (41) has a rotational axis (40) at the center position on the inner surface. The plurality of blades (42) are arranged so as to be symmetrical in the outer periphery of the hub (41), and each blade (42) has a front edge (421) and a rear edge. (422), a radially inner edge (423), a radially outer edge (424) are formed, and each adjacent two blades (42) in the longitudinal direction parallel to the rotational axis (40) are vertically proportional to each other. By being formed so as to overlap in the direction, each blade (42) is formed with the first vertical overlap zone (A1) and the second vertical overlap zone (A2), and the first vertical overlap zone (A1). ) Extends out from the front edge (421) and the radially inner edge (423). Is formed so as not to reach the radially outer edge (424) of the blade (42), and the second vertical overlap zone (A2) is further separated from the rear edge (422) and the radially inner edge (423). Although it is formed so as to extend outward, it is formed so as not to reach the radially outer edge (424) of the blade (42), thereby simultaneously increasing the amount of wind entering by the impeller (4). An impeller structure for an axial-flow heat dissipating fan, characterized in that it can reduce the noise of air blowing.   The rear edge (422) of the blade (42) projects on the adjacent blade (42) in the vertical direction to form a rear edge projection line (L1), and the first vertical overlap zone (A1) is the front edge. (421), The impeller structure of an axial-flow-type heat radiating fan according to claim 1, wherein the impeller structure is formed between a radially inner edge (423) and a rear edge projection line (L1).   The front edge (421) and the radial inner edge (423) intersect to form a front base point (I1), and the rear edge projection line (L1) intersects with the front edge (421) to form a first overlapping point (P1). The length from the front base point (I1) to the first overlapping point (P1) is 1/5 to 4/5 of the actual total length of the front edge (421). The impeller structure of the described axial flow type heat dissipation fan.   The front edge (421) and the radial inner edge (423) intersect to form a front base point (I1), and the rear edge projection line (L1) intersects with the radial inner edge (423) to meet the second overlapping point (P2). ), And the length from the front base point (I1) to the second overlapping point (P2) is from 1/6 to 5/6 of the actual total length of the radial inner edge (423). Item 3. An impeller structure of an axial-flow heat radiating fan according to Item 2.   The front edge (421) of the blade (42) is projected on the adjacent blade (42) in the vertical direction to form a front edge projection line (L2), and the second vertical overlap zone (A2) is the rear edge ( 422), the impeller structure of the axial-flow-type heat radiating fan according to claim 1, wherein the impeller structure is formed between a radially inner edge (423) and a front edge projection line (L2).   The rear edge (422) and the radially inner edge (423) meet to form a rear base point (O1), and the front edge projection line (L2) intersects with the rear edge (422) to form a third overlapping point. (P3) is formed, and the length from the rear base point (O1) to the third overlapping point (P3) is 1/5 to 4/5 of the actual total length of the rear edge (422). The impeller structure of the axial-flow-type heat radiating fan according to claim 5.   The rear edge (422) and the radial inner edge (423) intersect to form a rear base point (O1), and the front edge projection line (L2) intersects the radial inner edge (423) to meet the fourth overlapping point ( P4) is formed, and the length from the front base point (O1) to the fourth overlapping point (P4) is 1/6 to 5/6 of the actual total length of the radial inner edge (423). The impeller structure of the axial-flow-type heat radiating fan according to claim 5.   The front edge (421) and the rear edge (422) of each adjacent two blades (42) in the longitudinal direction parallel to the rotation axis (40) are overlapped in the longitudinal direction to form an angle (θ1), 2. The impeller structure for an axial-flow heat dissipating fan according to claim 1, wherein the angle ([theta] 1) is formed to be between 10 [deg.] And 90 [deg.].   The front end point (I2) of the front edge (421) of each blade (42) and the rear end point (O2) of the rear edge (422) are connected to the radial plane (P) of the hub (41). A straight line (L) is formed, an inclination angle (θ2) is formed between the straight line (L) and the radial plane (P), and the inclination angle (θ2) is interposed between 10 ° and 70 °. The impeller structure of an axial-flow-type heat radiating fan according to claim 1, wherein the impeller structure is formed as follows.

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