JP5111582B2 - Centrifugal fan, air conditioner equipped with the same and centrifugal fan mold - Google Patents

Description

  The present invention relates to a centrifugal fan, an air conditioner including the centrifugal fan, and a mold for the centrifugal fan.

A centrifugal fan used in an air conditioner or the like is required to have high efficiency for energy saving.
As background art of this technical field, there is JP-A-2007-170331 (Patent Document 1). This publication describes a technology for providing a centrifugal fan that can suppress the generation of a separation flow in the vicinity of the leading edge of the blades and suppress the pressure loss and noise generation of the air flow, and an air conditioner using the centrifugal fan. Has been. Specifically, the blade disposed between the main plate and the side plate is configured such that the inlet angle at the leading edge gradually decreases from the main plate side toward the side plate side, so that the flow is relative to the blade. There is almost no collision, and peeling in the vicinity of the leading edge is suppressed.

  Moreover, there exists Unexamined-Japanese-Patent No. 2007-170771 (patent document 2). This publication describes a technology for providing a centrifugal fan and an air conditioner using the centrifugal fan that can suppress the deviation of the wind speed distribution of the flow in the blow-out section. Specifically, the wings arranged between the main plate and the side plate are arranged such that the trailing edge of the main plate side is arranged on the rotational direction side of the trailing edge of the side plate side, and the trailing edge skew angle is in a predetermined angle range. By adopting the configuration, the uneven distribution of the wind velocity distribution in the blowout portion of the centrifugal fan is suppressed.

JP 2007-170331 A JP 2007-170771 A

  The centrifugal fans described in Patent Literature 1 and Patent Literature 2 have achieved high efficiency by designing the blade shape to match the flow. However, these centrifugal fans become wings having a complicated and complicated three-dimensional shape, and are manufactured by molding the wing, the side plate, and the main plate separately and then joining them. Therefore, there is a problem that the manufacturing cost increases.

  An object of the present invention is to realize a highly efficient centrifugal fan at a low cost.

  In order to solve the above-mentioned problems, the present invention comprises a main plate that is rotationally driven, a side plate that has an air inlet, and a plurality of blades that are disposed between the main plate and the side plate. The side plate side blade inlet angle is smaller than the main plate side blade inlet angle, the side plate side rear edge end portion is disposed on the counter-rotating side of the main plate side rear edge end portion, and the main plate and the In the centrifugal fan that integrally molds the blade, the front edge end portion on the side plate side as viewed from the direction of the rotation axis is disposed on the counter-rotation side with respect to the pressure surface on the joint projection surface on the main plate side, and the plurality of blades The plurality of blades are arranged on the main plate so that a mold for molding one of the blades and another blade adjacent to the one blade is removed in the air blowing direction.

  According to the present invention, a highly efficient centrifugal fan can be realized at low cost.

1 is a perspective view of a centrifugal fan in Embodiment 1. FIG. It is the figure which looked at the blade | wing of the centrifugal fan in Example 1 from the rotating shaft direction and the suction side direction. It is the figure which looked at 1 blade | wing of the centrifugal fan in Example 1 from the rotating shaft direction and the suction side direction. It is the figure which looked at 1 blade | wing of the centrifugal fan in Example 1 from the rotating shaft direction and the suction side direction. It is explanatory drawing of the metal mold | die used for shaping | molding of the centrifugal fan in Example 1, and is a longitudinal cross-sectional view which passes along a rotating shaft. It is explanatory drawing of the metal mold | die used for shaping | molding of the centrifugal fan in Example 1, and is a cross-sectional view in the plane which passes along the point B perpendicular | vertical to a rotating shaft. It is a perspective view of a side plate. It is a perspective view of the integrally molded component of a main plate and a wing. FIG. 3 is a longitudinal sectional view passing through the rotation axis of the centrifugal fan in the first embodiment. It is the figure which looked at the blade | wing of the centrifugal fan in Example 2 from the rotating shaft direction and the suction side direction. It is explanatory drawing of the metal mold | die used for shaping | molding of the centrifugal fan in Example 2, and is a cross-sectional view in the plane which passes along the point D perpendicular | vertical to a rotating shaft. It is explanatory drawing of the metal mold | die used for shaping | molding of the centrifugal fan in Example 2, and is the cross-sectional view cut | disconnected in the position between the main plate 3 and the side plate 2. FIG. It is the figure which looked at the blade | wing of the centrifugal fan in Example 3 from the rotating shaft direction and the suction side direction. It is an experimental result which shows the effect of high efficiency of the centrifugal fan in Example 3. It is an air conditioning apparatus in Example 4.

  Embodiments will be described below with reference to the drawings.

  In this embodiment, an example of a highly efficient and low cost centrifugal fan will be described. The first embodiment will be described with reference to FIGS.

  FIG. 1 is a perspective view of a centrifugal fan according to the first embodiment. Reference numeral 1 denotes a wing, 2 denotes a side plate, and 3 denotes a main plate. Reference numeral 4 denotes a rotating shaft, and 5 denotes the rotating direction of the centrifugal fan. A plurality of blades 1 are provided between the side plate 2 and the main plate 3. Air is sucked from the suction port 36 of the side plate 2 and is blown in the centrifugal direction from between the blade 1 and the adjacent blade 1. In the centrifugal fan, the blade 1, the side plate 2, and the main plate 3 are connected. When the main plate 3 connected to a motor (not shown) is driven to rotate by the motor, the centrifugal fan rotates.

FIG. 2 is a view of the blades of the centrifugal fan according to the first embodiment when viewed from the rotation axis direction and the suction side direction. Here, two wings are shown. The front side in the rotation direction of the blade 1 is referred to as a front edge, and the rear side is referred to as a rear edge. Reference numeral 6 denotes a side plate side rear edge end portion, and 7 denotes a main plate side rear edge end portion. Reference numeral 8 denotes a side plate side front edge end portion, and 9 denotes a main plate side front edge end portion. Reference numeral 10 denotes a pressure surface of the blade 1, and 11 denotes a suction surface of the blade 1. In FIG. 2, the surface where the side plate 2 and the blade 1 are joined is projected onto a cross section perpendicular to the rotational axis direction, and the surface where the main plate 3 and the blade 1 are joined is projected onto a cross section perpendicular to the rotational axis direction. The wing | blade 1 is shown using the done surface. Hereinafter, the former is referred to as a side projection projection surface and the latter is referred to as a main projection projection plane. The front edge portion and the rear edge portion are connecting portions of the pressure surface 10 and the suction surface 11, respectively. Reference numeral 12 denotes a camber line (side plate camber line) on the side projection side viewed from the rotation axis direction, and reference numeral 13 denotes a camber line (main plate side camber line) on the main projection side seen from the rotation axis direction. Show. The camber line refers to a center line connecting points that are equidistant from a line that draws the pressure surface 10 and a line that draws the suction surface 11 when the blade 1 is cut in a cross section perpendicular to the rotation axis direction. β _s1 represents the side plate side blade inlet angle, and β _h1 represents the main plate side blade inlet angle. The blade entrance angle is defined as the angle formed by the tangent at the leading edge of the camber line and the tangent at the leading edge of the arc passing through the leading edge and centering on the rotation axis. The blade 1 is twisted from the main plate 3 to the side plate 2 so as to incline to the counter-rotating side.

FIG. 3a is a view of one blade of the centrifugal fan according to the first embodiment when viewed from the rotation axis direction and the suction side direction. A is a point where the blade angle on the suction surface 11 side in the joint projection surface on the side plate side is the minimum β _{ss_min,} and B is a blade angle on the pressure surface 10 side in the joint projection surface on the main plate side is the maximum β _{ps_max.} Indicates a point. All points are set except for the leading edge. The leading edge refers to a substantially arc or curve connecting the pressure surface 10 and the suction surface 11 at the front edge end of the blade 1. Reference numeral 14 denotes a tangent at the point A on the suction surface 11, and 15 denotes a tangent at the point B on the pressure surface 10. The blade angle is such that when a tangent at a certain point in the curve of the blade 1 and an arc passing through the trailing edge and centering on the rotation axis 4 intersect, the tangent at a certain point in the curve and the tangent at the intersection of the arc It is defined by the angle between

FIG. 3b is an alternative to the way of setting point B in FIG. 3a. P indicates a point at which the blade angle at the central plane (main plate side camber line) on the main plate side joint projection plane is the maximum _{β_max,} and is set except for the leading edge. The point B may be determined as a point on the pressure surface 10 that is the shortest distance from the point P on the joining projection plane on the main plate side. The center plane is a plane at the center of the pressure plane 10 and the suction plane 11 and is defined by connecting the camber line obtained when the blade 1 is cut in a cross section perpendicular to the rotation axis direction from the side plate 2 to the main plate 3. . Reference numeral 37 denotes a tangent at the point P. In FIG. 3 b, the point P is shown on the camber line 13. The blade 1 is designed to be thickened on the pressure surface side and the suction surface side after determining the camber line. Therefore, as compared with FIG. 3a, it is easier to design the point B after the point P is determined.

  FIG. 4 is an explanatory view of a mold used for forming the centrifugal fan in the embodiment 1, and is a longitudinal sectional view passing through the rotation axis. Reference numeral 16 denotes a mold that moves in the direction of the rotation axis, and moves in the direction of the arrow 18. A mold 17 moves in the blowing direction, and moves in the direction of the arrow 19. There is one die 17 that moves in the blowing direction for each blade 1. One blade 1 is formed by one mold 16 and two molds 17. The centrifugal fan of Example 1 is molded by these molds 16 and 17.

  FIG. 5 is an explanatory view of a mold used for forming the centrifugal fan in the embodiment 1, and is a cross-sectional view in a plane perpendicular to the rotation axis and passing through the point B. Along with the mold, a joining projection surface on the main plate side of the blade 1 and a joining projection surface on the side plate side are also shown. Reference numeral 20 denotes a boundary for dividing the mold 16 and the mold 17. The boundary point C indicates a point on the pressure surface on the joining projection surface on the main plate side, and is located on the blowing side from the point B. The mold 17 moves in the direction of the arrow 21. In FIG. 5, the mold 17 shows only one space between the blades.

  In FIG. 5, the point C is shown on the pressure surface 10 on the joint projection surface on the main plate side, but the boundary dividing the mold 16 and the mold 17 exists in an arbitrary cross section between the main plate 3 and the side plate 2. To do.

  6 is a perspective view of a side plate, and FIG. 7 is a perspective view of an integrally molded component of a main plate and a wing. The side plate 2 having the air suction port 36 has a gently curved cross section cut along a plane passing through the rotation shaft 4. Thereby, air can be made difficult to peel. The centrifugal fan of FIG. 1 is manufactured by joining the side plate 2 and the blade 1.

FIG. 8 is a longitudinal sectional view passing through the rotation axis of the centrifugal fan in the first embodiment. Reference numeral 23 denotes a bell mouth. Reference numeral 24 denotes a flow on the side plate side, and reference numeral 25 denotes a flow on the main plate side. C _h is the absolute velocity component of the main plate side, C _rh is the radial velocity component of the main plate side, C _zh shows the axial velocity component of the main plate side. C _s represents the absolute velocity component on the side plate side, C _rs represents the radial velocity component on the side plate side, and C _zs represents the axial velocity component on the side plate side.

  The configuration, operation, and effect of the centrifugal fan according to the present embodiment will be described with reference to FIGS.

Since the centrifugal fan blows out the sucked air almost at a right angle, the air flow is biased toward the main plate. As shown in FIG. 8, the flow 25 on the main plate side is faster than the flow 24 on the side plate side, and the radial velocity component C _rh on the main plate side is larger than the radial velocity component C _rs on the side plate side. Therefore, in FIG. 2, the side plate side blade inlet angle β _s1 <the main plate side blade inlet angle β _h1 . As a result, the blades can follow the flow on the side plate side and the main plate side, and flow separation is suppressed. As a result, the centrifugal fan becomes highly efficient.

  In FIGS. 2, 3 a, and 3 b, the side plate side rear edge end portion 6 is disposed on the counter-rotating side with respect to the main plate side rear edge end portion 7. By setting it as such a structure, since a wing | blade force acts toward the side plate side from the main plate side in the blower outlet vicinity, it can suppress that a low energy fluid accumulates on the side plate side and the suction surface side. Thereby, while the sucked air flows from the front edge to the rear edge, the air can be guided from the main plate side to the side plate side, and air can be prevented from being biased toward the main plate side. As a result, the centrifugal fan becomes highly efficient.

  2, 3 a, and 3 b, the main plate side front edge end portion 9 is disposed closer to the rotating shaft 4 than the side plate side front edge end portion 8. By adopting such a configuration, the air flow in which the air sucked from the side plate side is biased toward the main plate side can be quickly captured by the front edge on the main plate side, and the sucked air can be efficiently flowed to the rear edge. be able to.

  2, 3 a, and 3 b, the side plate side front edge end portion 8 is arranged on the counter-rotating side with respect to the pressure surface 10 on the main plate side. That is, in these drawings, the main projection side projection projection surface and the side projection projection surface are not crossed. Further, the wing 1 is arranged on the main plate 3 so that the mold 17 for molding the wing 1 and the adjacent wing 1 is removed in the air blowing direction (arrow 21). Specifically, the blade 1 is arranged so that the tangent line 14 and the tangent line 15 are parallel or intersect the point A or the point B on the rotating shaft 4 side. In this embodiment, an angle α formed by the tangent line 14 and the tangent line 15 is an acute angle. As the number of centrifugal fan blades 1 decreases, the angle α increases, and may be an obtuse angle such as 120 °. In short, the tangent line 14 and the tangent line 15 may be parallel or spread toward the outer periphery. However, since the mold 17 cannot pass, it must not exceed 180 °.

  In the case of the blade 1 having the points A and B as described above, if the mold is divided on the discharge side from the point B on the pressure surface 10 on the joint projection surface on the main plate side, the mold 17 is indicated by the arrow 21. It becomes possible to move in the direction, and the centrifugal fan using the mold 16 and the mold 17 shown in FIGS. 4 and 5 can be molded. In the present embodiment, a boundary point C on the blowing side with respect to the point B is provided. As a result, as shown in FIG. 7, the main plate 3 and the blade 1 can be integrally molded, and the cost can be reduced compared to a centrifugal fan in which the blade 1, the side plate 2, and the main plate 3 are separately formed.

In the present embodiment, an example of providing a centrifugal fan with higher efficiency at a low cost will be described. A second embodiment of the present invention will be described with reference to FIGS.
FIG. 9 is a view of the blade of the centrifugal fan according to the second embodiment as viewed from the direction of the rotation axis and the direction of the suction side. A description of the same symbols as those in FIG. 2 is omitted. 22 is parallel to the tangent line 14 at the point A where the blade angle on the suction surface 11 side on the suction surface 11 side on the side plate side of the blade 1 becomes the minimum β _{ss_min,} and the pressure surface on the joint projection surface on the main plate side of the adjacent blade The tangent at 10 is shown. Point D indicates a contact point between the tangent line 22 and the pressure surface 10.

  FIG. 10 is an explanatory view of a mold used for forming the centrifugal fan in the embodiment 2, and is a cross-sectional view in a plane perpendicular to the rotation axis and passing through the point D. Along with the mold, a joining projection surface on the main plate side of the blade 1 and a joining projection surface on the side plate side are also shown. The boundary point E indicates a point on the pressure surface on the joining projection surface on the main plate side, and is located on the outlet side from the point D. The mold 17 moves in the direction of the arrow 21. In FIG. 10, the mold 17 shows only one space between the blades.

  FIG. 11 is an explanatory view of a mold used for forming the centrifugal fan in the second embodiment, and is a cross-sectional view cut at a certain position between the main plate 3 and the side plate 2. A joint projection surface on the main plate side, a joint projection surface on the side plate side, and a cross-sectional view are shown together with the mold. In FIG. 11, the point E is arranged on a cross section of the blade 1. The boundary dividing the mold 16 and the mold 17 exists in an arbitrary cross section between the main plate 3 and the side plate 2.

The configuration, operation, and effect of the centrifugal fan of the present invention will be described with reference to FIGS. 9 to 11 described above.
In the centrifugal fan of this embodiment, the main plate side blade inlet angle β _h1 is set larger in FIG. 9 than in the case of FIG. Thereby, it becomes possible to set it as the wing | blade shape along the flow 25 by the side of the main plate, and flow separation is suppressed. As a result, the centrifugal fan becomes more efficient.

  In the present embodiment, the front edge on the main plate side is bent more toward the rotating shaft 4 than in the first embodiment. For this reason, when the tangent is determined at the point B that is the maximum blade angle as in the first embodiment, the tangent and the tangent 14 intersect outside the centrifugal fan. If it does so, the metal mold | die 17 cannot move to the blowing direction. In the embodiment, when a boundary for dividing the mold 16 and the mold 17 is determined, a point D where a tangent line 22 parallel to the tangent line 14 is in contact with the pressure surface 10 side of the joining projection surface on the main plate side is used. In the case of the blade 1 having the point D, the mold 17 can be moved in the direction of the arrow 21 if the mold is divided on the blowing side from the point D on the pressure surface 10 on the joining projection plane on the main plate side. Thus, the centrifugal fan using the mold 16 and the mold 17 shown in FIG. 9 can be molded. In this embodiment, a boundary point E on the outlet side from the point D is provided. Thereby, the main plate 3 and the blade 1 can be integrally molded using the mold 16 and the mold 17, and the cost can be reduced as compared with a centrifugal fan in which the blade 1, the side plate 2, and the main plate 3 are separately molded.

  In the present embodiment, an example of providing a centrifugal fan with higher efficiency at a low cost will be described. A third embodiment of the present invention will be described with reference to FIGS.

FIG. 12 is a view of the blades of the centrifugal fan according to the third embodiment when viewed from the rotation axis direction and the suction side direction. Reference numeral 26 denotes a joining projection plane on the main plate side. R _1h is the radius of an arc passing through the main plate side front edge end 9 with the rotation axis 4 as the center, and R _1s is the radius of the arc passing through the side plate side front edge end 8 with the rotation axis as the center. L _h is a chord length connecting the main plate side front edge end portion 9 and the main plate side rear edge end portion 7, and L _s is a chord length connecting the side plate side front edge end portion 8 and the side plate side rear edge end portion 6.

FIG. 13 is an experimental result showing the effect of increasing the efficiency of the centrifugal fan in the third embodiment. The experimental result shown as conventional in FIG. 13 is a conventional centrifugal fan that does not employ this embodiment. In this centrifugal fan, the side plate side rear edge end portion 6 is arranged on the rotation side with respect to the main plate side rear edge end portion 7 so that the side plate side blade inlet angle β _s1 > the main plate side blade inlet angle β _h1 . In the measured flow rate range, it can be confirmed that the present example is more efficient than the conventional example.

  The configuration, operation, and effect of the centrifugal fan of the present invention will be described with reference to FIGS. 12 and 13 described above.

Centrifugal fan of this embodiment, similar to the first embodiment shown in FIG. 8, the main plate side of the stream 25 is faster than the flow 24 of the side plate side, the radial velocity component C _rh of the main plate side of the side plate radius Larger than the direction velocity component C _rs . Therefore, it is the main plate that dominates the efficiency of the centrifugal fan. Therefore, as shown in FIG. 12, a long chord length L _h on the main plate side is ensured by setting radius R _1h <radius R _1s . In this embodiment, the trailing edge of the blade 1 extends to the outermost diameter of the main plate 3. By adopting such a configuration, it is possible to suppress the separation on the main plate side and improve the efficiency of the blade. As a result, the centrifugal fan becomes more efficient.

In addition, since the curvature of the air flow is large on the side plate suction side, the flow is easily separated on the side plate 2 side and the suction surface 11 side. Therefore, as shown in FIG. 12, the side plate side front edge end portion 8 is overlapped with the main plate side joint projection surface 26. As a result, the chord length L _s can be secured longer than in the above embodiment. With such a configuration, the air flow can be made to follow the wing 1 at the side plate side front edge end portion 8, and the air flow on the side plate side is more difficult to peel off. As a result, the centrifugal fan becomes more efficient.

  The centrifugal fan of this embodiment is manufactured by joining integrally molded parts of the side plate 2, the main plate 3, and the blade 1 shown in FIGS. At the time of joining, the side plate 2 applies a load to the blade 1 in the direction of the rotation axis. Since the blade 1 of the centrifugal fan according to the first and second embodiments has a shape inclined in the anti-rotation direction, a bending moment is applied to the blade 1 and the main plate 3 at the time of joining. In the third embodiment, the side plate-side front edge end portion 8 is overlapped with the main plate-side joining projection surface 26, and thus the blade 1 on the rotating shaft side from the vicinity of the side plate-side front edge end portion 8 has a blade shape substantially perpendicular to the main plate 3. With such a configuration, the strength of the blade is improved, and deformation due to a bending moment at the time of joining can be suppressed. As a result, it is possible to suppress the yield due to the falling of the blade when an excessive bending moment is applied, which contributes to the cost reduction of the centrifugal fan.

In this embodiment, _let F be the point where the blade angle on the suction surface 11 side of the joint projection surface on the side plate side is the minimum β _{ss_min} . Also, _let G be the point where the blade angle on the pressure surface 10 side in the joint projection plane on the main plate side is the maximum β _{ps_max} . The method of setting the point G may be set at a point _where the blade angle at the center plane (main plate side camber line) on the main plate side joining projection plane is the maximum _{β_max} in the above embodiment. The angle γ formed by the tangent at the point F and the tangent at the point G corresponds to the angle α in the above embodiment.

  In this embodiment, an example in which the centrifugal fan of any of Embodiments 1 to 3 is mounted on an air conditioner will be described. A fourth embodiment of the present invention will be described with reference to FIG.

  FIG. 14 shows an air conditioner according to the fourth embodiment. Reference numeral 27 denotes a centrifugal fan according to any one of the first to third embodiments, 28 denotes a bell mouth, 29 denotes a motor, 30 denotes a heat exchanger, 31 denotes a housing, 32 denotes a grill and a filter, and 33 denotes an outlet.

  In FIG. 14, the bell mouth 28 is disposed so as to overlap the side plate 2 of the centrifugal fan 27 with a dimension 34. The centrifugal fan 27 is driven by a motor 29. The flow passes through the grille and the filter 32 as indicated by 35, is pressurized by the centrifugal fan 27, and is discharged from the air outlet 33 to the atmosphere via the heat exchanger 30. Embodiment 4 of the present invention can provide a highly efficient air conditioner.

1 Blade 2 Side plate 3 Main plate 4 Rotating shaft 5 Rotating direction 6 Side plate side rear edge end portion 7 Main plate side rear edge end portion 8 Side plate side front edge end portion 9 Main plate side front edge end portion 10 Pressure surface 11 Negative pressure surface 12 Side plate side camber Line 13 Main plate side camber lines 14, 15, 22 Tangent 16 Mold (mold moving in the direction of the rotation axis)
17 Mold (Mold moving in the blowing direction)
18, 19, 21 Arrow 20 Boundary 23, 28 Bell mouth 24 Flow on the side plate 25 Flow on the main plate 26 Joint projection surface 27 on the main plate 27 Centrifugal fan 29 Motor 30 Heat exchanger 31 Housing 32 Grill and filter 33 Air outlet 34 maximum blade angle α tangent 14 at the maximum blade angle beta _{_max} central plane at the minimum blade angle beta _{Ps_max} pressure surface on the dimensions 35 stream 36 inlet beta _s1 shroud side blade inlet angle beta _h1 main plate side blade inlet angle beta _{Ss_min} suction side on the tangent Angle R _1h , R _1s radius L _h , L _s chord length formed by 15

Claims (11)

A main plate that is driven to rotate, a side plate that has an air inlet, and a plurality of blades that are arranged between the main plate and the side plate,
The blade inlet angle on the side plate side of the blade is smaller than the blade inlet angle on the main plate side,
The rear edge portion on the side plate side is disposed on the counter-rotating side than the rear edge end portion on the main plate side,
In the centrifugal fan that integrally molds the main plate and the blade,
The front edge end on the side plate side as viewed from the direction of the rotation axis is disposed on the counter-rotation side with respect to the pressure surface on the joint projection surface on the main plate side, and one of the plurality of blades and the one blade The centrifugal fan, wherein the plurality of blades are arranged on the main plate so that a mold for molding another adjacent blade is removed in the air blowing direction. In claim 1,
The blade angle is minimized at the tangent line at the point where the blade angle is maximized on the pressure projection surface on the main plate side of the other blade and the negative pressure surface on the joint projection surface on the side plate side of the one blade. A centrifugal fan, characterized in that a tangent at a point intersects on a parallel or rotating shaft side. In claim 2,
Instead of the tangent line at the point where the blade angle is maximized at the pressure surface on the joint projection surface of the other blade on the main plate side, the blade angle is maximum on the center plane of the joint projection surface on the main plate side of the other blade. The tangent at the point on the pressure surface that is the shortest distance from the point and the tangent at the point at which the blade angle is the smallest on the suction projection surface on the side plate side of the one blade are parallel or rotational axes. Centrifugal fan characterized by crossing at the side. In claim 1,
A mold that moves in the direction of the rotation axis;
Molded with a plurality of molds moving in the blowing direction,
The boundary point on the pressure surface of the joint projection plane on the main plate side of the other blade that divides the mold moving in the rotation axis direction and the plurality of molds moving in the blowing direction is the one blade. Outlet side of contact point on tangent line on pressure surface of joint projection surface of main plate side of other blades parallel to tangent line at point of blade pressure at minimum suction surface on joint projection surface on side plate side Centrifugal fan characterized by being arranged in. In claim 2,
A mold that moves in the direction of the rotation axis;
Molded with a plurality of molds moving in the blowing direction,
The boundary point on the pressure surface of the joint projection surface on the main plate side of the other blade that divides the mold moving in the rotation axis direction and the plurality of molds moving in the blowing direction is the other blade. A centrifugal fan, characterized in that the centrifugal fan is arranged on a blow-out side from a point at which a blade angle becomes maximum at a pressure surface on a joint projection plane on the main plate side. In claim 3,
A mold that moves in the direction of the rotation axis;
Molded with a plurality of molds moving in the blowing direction,
A boundary point on the pressure surface in the joint projection plane on the main plate side of the other blade that divides the mold moving in the rotation axis direction and the plurality of molds moving in the blowing direction is on the pressure surface. A centrifugal fan, characterized in that the centrifugal fan is arranged on the outlet side of the point. In any one of Claims 1 thru | or 6,
A centrifugal fan, wherein a front edge end portion on the side plate side as viewed from the direction of the rotation axis is overlapped with a joint projection surface on the main plate side.   The centrifugal fan according to any one of claims 1 to 7, a heat exchanger disposed on an outer peripheral side of the centrifugal fan, a housing for housing the centrifugal fan and the heat exchanger, and disposed on an air inlet side Air conditioner with a bell mouth. In the mold for molding the centrifugal fan of claim 1,
A mold that moves in the direction of the rotation axis;
A plurality of molds moving in the blowing direction,
The boundary point at the pressure surface on the joint projection plane on the main plate side of the other blade that divides the mold moving in the rotation axis direction and the plurality of molds moving in the blowing direction is the one blade. Outlet side of contact point on tangent line on pressure surface of joint projection surface of main plate side of other blades parallel to tangent line at point of blade pressure at minimum suction surface on joint projection surface on side plate side A centrifugal fan mold characterized by being arranged in In the mold for molding the centrifugal fan according to claim 2,
A mold that moves in the direction of the rotation axis;
A plurality of molds moving in the blowing direction,
The boundary point on the pressure plane of the joint projection surface on the main plate side of the other blade that divides the mold moving in the rotation axis direction and the plurality of molds moving in the blowing direction is the other blade. A centrifugal fan mold, wherein the mold is arranged on a blow-out side from a point at which a blade angle is maximum on a pressure surface on a joint projection plane on the main plate side. In the mold for molding the centrifugal fan according to claim 3,
A mold that moves in the direction of the rotation axis;
A plurality of molds moving in the blowing direction,
A boundary point on the pressure surface on the joint projection plane on the main plate side of the other blade that divides the mold moving in the rotation axis direction and the plurality of molds moving in the blowing direction is on the pressure surface. A centrifugal fan mold characterized by being arranged on the outlet side of the point.

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