TW202037853A - Centrifugal blower, blowing device, air-conditioning device, and refrigeration cycle device - Google Patents

Abstract

The present invention makes it possible to efficiently increase the pressure of an airstream even in a dual-suction centrifugal blower. Provided is a centrifugal blower wherein, when a peripheral wall opposing a first blade section and a peripheral wall opposing a second blade section are defined respectively as a first peripheral wall and a second peripheral wall, the position of the first peripheral wall where the distance between the first peripheral wall and a rotary shaft of an impeller in a direction orthogonal to the axial direction of the rotary shaft is the greatest in the axial direction is defined as a first maximum part, and the position of the second peripheral wall where the distance between the second peripheral wall and the rotary shaft in a direction orthogonal to the axial direction is the greatest in the axial direction is defined as a second maximum part, the first maximum part is formed closer to a main plate than a center position between the main plate and a first side plate in the axial direction, and the second maximum part is formed closer to the main plate than a center position between the main plate and a second side plate in the axial direction.

Description

Centrifugal fan, air blowing device, air conditioner and refrigeration cycle device

The invention relates to a double-suction centrifugal fan with a volute, an air blowing device, an air-conditioning device and a refrigerating cycle device including the centrifugal fan.

The previous centrifugal fan system includes: an impeller, which is composed of a main plate and a plurality of wings on a disk; and a volute, which houses the impeller, and forms a suction port through which air flowing into the impeller passes. The air flow blown out by the rotation of the impeller has a velocity distribution in the rotation axis of the impeller, and the air velocity on the main plate side is greater than the suction port side. The previous centrifugal fan is in the rotation axis of the impeller, and the distance between the impeller and the peripheral wall of the scroll is fixed. Therefore, the air flow from the main board side with higher speed collides with the peripheral wall of the scroll, and it becomes in the volute and cannot be efficient The main reason for a good boost airflow. Here, a single suction type centrifugal fan is proposed that efficiently boosts the airflow by increasing the distance between the impeller and the peripheral wall of the scroll where the air velocity discharged from the impeller is relatively high (for example, refer to Patent Document 1). [Patent Literature]

[Patent Document 1] JP 01-108399 Gazette

However, the centrifugal fan of Patent Document 1 is a single suction centrifugal fan. Compared with a single-suction type centrifugal fan, in a double-suction type centrifugal fan, air flows from suction ports formed at the two ends of the rotating shaft of the impeller merge on the main plate side. Therefore, in a double-suction type centrifugal fan, when the air flow hits the scroll wall, it becomes a turbulent flow. However, there is a problem that the airflow cannot be boosted efficiently by increasing the distance between the impeller and the scroll wall.

The present invention was developed to solve the above-mentioned problems, and its purpose is to obtain a centrifugal fan, blower, air conditioner, and refrigeration cycle device that can efficiently boost airflow even if it is a double-suction centrifugal fan.

The centrifugal fan system of the present invention includes an impeller and a volute. The impeller system has: a main plate, which is driven by rotation; a first fan portion, consisting of a ring-shaped first side plate arranged opposite to the main plate and a gap between the main plate and the first side plate. A plurality of blades are formed; and the second blade portion is composed of a ring-shaped second side plate arranged opposite to the main board on the side opposite to the side where the first side plate is arranged with respect to the main board and arranged on the main board and the second 2. The volute is composed of a plurality of fan blades between the side plates; the volute has: a peripheral wall formed in a scroll shape; a first side wall formed with a first suction port facing the plate surface of the main plate on the side where the first side plate is arranged; And the second side wall is formed with a second suction port facing the plate surface of the main plate on the side where the second side plate is arranged; accommodating the impeller; when the peripheral wall facing the first blade portion is defined as the first peripheral wall, it will be The peripheral wall facing the second blade portion is defined as the second peripheral wall. The distance between the first peripheral wall and the rotating shaft in the direction orthogonal to the axial direction of the rotating shaft of the impeller is the largest in the axial direction. The position of the first peripheral wall is defined as the first largest part. The distance between the second peripheral wall and the axis of rotation in the direction orthogonal to the axial direction is set in the axial direction to become the largest second peripheral wall position , When defined as the second largest part, the first largest part is formed in the axial direction, which is closer to the main board side than the middle position between the main board and the first side plate, and the second largest part is formed in the axial direction, which is shorter than the main board and The middle position between the second side plates is also formed close to the main board side.

The air blowing device of the present invention includes the above-mentioned centrifugal fan, and a casing accommodating the centrifugal fan.

The air conditioner of the present invention includes the above-mentioned centrifugal fan, and a heat exchanger arranged at a position facing the outlet of the centrifugal fan.

The refrigeration cycle device of the present invention includes the above-mentioned centrifugal fan. [Invention Effect]

According to the present invention, the first largest part of the centrifugal fan is formed in the axial direction, which is closer to the main board side than the middle position between the main plate and the first side plate, and the second largest part is formed in the axial direction, which is shorter than the main plate and the second side plate. The middle position between the side plates is also formed close to the main board side. The centrifugal fan uses the first largest part and the second largest part. The distance between the impeller and the peripheral wall of the volute is greater on the side plate side than the main plate side, so that when the air flow from the suction port merges on the main plate side, it is used to the peripheral wall side The turbulence of the airflow is suppressed. Therefore, the centrifugal fan system reduces the pressure loss caused by the air flow turbulence, and can efficiently boost the air flow in the volute.

Hereinafter, the centrifugal fan 1 of the embodiment will be described with reference to drawings and the like. In addition, the blower 30, the air conditioner 40, and the refrigerating cycle device 50 of the embodiment will also be described with reference to the drawings. Moreover, in the following drawings including FIG. 1, the relative size relationship and shape of each constituent member may be different from the actual ones. In addition, in the following drawings, those assigned the same number are the same or equivalent. This fact is in the full text of the patent specification and is regarded as common. Also, for ease of understanding, although it is appropriate to use terms that indicate directions (such as "up", "down", "right", "left", "front", "rear", etc.), these expressions are only for convenience Explain, and such a record does not limit the arrangement and direction of the device or parts.

Implementation mode 1. 〔Centrifugal fan 1〕 Fig. 1 is a perspective view of the centrifugal fan 1 of the first embodiment. FIG. 2 is a schematic diagram showing the relationship between the impeller 2 and the peripheral wall 4c of the volute 4 in FIG. 1. In addition, the centrifugal fan 1 is a double-suction type centrifugal fan that sucks air from both ends in the rotation axis RS of the impeller 2. The structure of the centrifugal fan 1 shown in FIG. 1 has the same structure on the opposite side. Therefore, the structure of the centrifugal fan 1 will be described using FIG. 1, and the structure of the centrifugal fan 1 on the opposite side of FIG. 1 is omitted from illustration. First, the basic structure of the centrifugal fan 1 will be explained using FIGS. 1 and 2. The centrifugal fan 1 is a centrifugal fan 1 of a multi-blade centrifugal type such as a multi-blade fan or a turbo fan, which has an impeller 2 for generating airflow and a volute 4 for accommodating the impeller 2.

(Impeller 2) The impeller 2 is driven to rotate by a motor or the like (not shown), and the centrifugal force generated by the rotation forces air to be forced out of the radial direction. As shown in Figs. 1 and 2, the impeller 2 has a disc-shaped main plate 2a and a plurality of fan blades 2d provided on the peripheral edge portion 2a1 of the main plate 2a. In addition, the main plate 2a may have a plate shape, and it may be a shape other than a disk shape, such as a polygonal shape. At the center of the main board 2a, a shaft portion 2b to which a motor (not shown) is connected is provided. The main board 2a is driven by a motor to rotate through the shaft 2b.

The plurality of blades 2d are arranged on the circumference with the shaft portion 2b as the center, and the base end is fixed to the main plate 2a. The plurality of blades 2d are located in the axial direction of the rotating shaft RS of the shaft portion 2b, and are provided on both sides of the main plate 2a. Each fan blade 2d is attached to the peripheral edge part 2a1 of the main plate 2a, and is arrange|positioned at predetermined intervals. Each blade 2d is formed in, for example, a curved rectangular plate shape, and is arranged along the radial direction or inclined at a predetermined angle with respect to the radial direction. Each blade 2d is formed as a two-dimensional wing with the same cross-sectional shape that is continuous in the axial direction of the rotation axis RS, but it may be a three-dimensional wing having a twisted shape. In addition, each fan blade 2d is set to stand approximately perpendicular to the main plate 2a, but the present invention is not limited to this structure, and each fan blade 2d may be set to be perpendicular to the main plate 2a. In terms of tilt.

The impeller 2 is set in the axial direction of the rotating shaft RS of the shaft portion 2b, and has an annular side plate 2c attached to the end portion of the plurality of blades 2d on the opposite side to the main plate 2a. The side plate 2c maintains the positional relationship of the tips of the blades 2d by connecting the plurality of blades 2d, and strengthens the plurality of blades 2d. Therefore, each of the plural blades 2d has one end connected to the main plate 2a and the other end connected to the side plate 2c, and is arranged between the main plate 2a and the side plate 2c.

The impeller 2 is formed in a cylindrical shape by a plurality of blades 2d arranged on the main plate 2a. In addition, the impeller 2 is in the axial direction of the rotating shaft RS of the shaft portion 2b, and on the side plate 2c side opposite to the main plate 2a, a suction port 2e for allowing gas to flow into the space surrounded by the main plate 2a and the plurality of blades 2d is formed . The impeller 2 is arranged on both sides of the plate surface constituting the main plate 2a, and blades 2d and side plates 2c are respectively arranged, and suction ports 2e are formed on both sides of the plate surface constituting the main plate 2a.

The impeller 2 is driven by a motor (not shown), and is driven to rotate with the rotating shaft RS as the center. When the impeller 2 rotates, the air outside the centrifugal fan 1 passes through the suction port 5 formed in the volute 4 and the suction port 2e of the impeller 2, and is sucked into the space surrounded by the main plate 2a and the plural fan blades 2d. Furthermore, the air sucked into the space enclosed by the main plate 2a and the plurality of blades 2d by the rotation of the impeller 2 passes between the blades 2d and the adjacent blades 2d, and is sent out radially outward.

(Volute 4) The volute 4 contains the impeller 2 and rectifies the air blown from the impeller 2. The volute 4 has a scroll part 41 and a discharge part 42.

(Scroll 41) The scroll portion 41 forms an air path that converts the dynamic pressure of the air flow generated by the impeller 2 into static pressure. The scroll portion 41 has: a side wall 4a that covers the impeller 2 from the axial direction of the rotating shaft RS constituting the shaft portion 2b of the impeller 2, and is formed with a suction port 5 for taking in air; and a peripheral wall 4c, a rotating shaft from the shaft portion 2b The RS radially surrounds the impeller 2. In addition, the scroll portion 41 has a tongue portion located between the discharge portion 42 and the scroll start portion 41a of the peripheral wall 4c to form a curved surface so that the airflow generated by the impeller 2 is guided to the discharge port 42a through the scroll portion 41 43. Moreover, the so-called radial direction of the rotation axis RS is a direction perpendicular to the rotation axis RS. The internal space of the scroll portion 41 formed by the peripheral wall 4c and the side wall 4a is a space in which the air blown from the impeller 2 flows along the peripheral wall 4c.

(Side wall 4a) The side walls 4a are in the axial direction of the rotating shaft RS of the impeller 2 and are arranged on both sides of the impeller 2. A suction port 5 is formed on the side wall 4a of the volute 4 so that air can circulate between the impeller 2 and the outside of the volute 4. The suction port 5 is formed in a circular shape, and the impeller 2 is arranged so that the center of the suction port 5 and the center of the shaft portion 2b of the impeller 2 approximately coincide. Moreover, the shape of the suction port 5 is not limited to a circular shape, and it may be another shape such as an ellipse. The volute 4 of the centrifugal fan 1 is located in the axial direction of the rotating shaft RS of the shaft portion 2b, on both sides of the main plate 2a, and has a double suction type casing in which the side wall 4a of the suction port 5 is formed. The volute 4 of the centrifugal fan 1 has two side walls 4a, and the side walls 4a are arranged to face each other. In detail, the volute system side wall 4a has a first side wall 4a1 and a second side wall 4a2. The first side wall 4a1 forms a first suction port 5a facing the plate surface of the main plate 2a on the side where the first side plate 2c1 is arranged. The second side wall 4a2 forms a second suction port 5b facing the plate surface of the main plate 2a on the side where the second side plate 2c2 is arranged. Furthermore, the above-mentioned suction port 5 is a general term for the first suction port 5a and the second suction port 5b.

The suction port 5 provided in the side wall 4a is formed by the bell mouth 3. The bell mouth 3 rectifies the gas sucked in by the impeller 2 to flow into the suction port 2e of the impeller 2. The bell mouth 3 is from the outside to the inside of the volute 4, and the diameter of the opening gradually decreases. With this structure of the side wall 4a, the air in the vicinity of the suction port 5 flows smoothly, and also flows into the impeller 2 from the suction port 5 efficiently.

(Zhoubi 4c) The peripheral wall 4c causes the airflow generated by the impeller 2 to pass through the scroll portion 41 along the curved wall surface to be guided to the discharge port 42a. The peripheral wall 4c is a wall provided between the side walls 4a facing each other, and forms a curved surface in the rotation direction R of the impeller 2. The peripheral wall 4c is arranged in a direction perpendicular to the axial direction of the rotating shaft RS of the impeller 2. The peripheral wall 4c covers the impeller 2 in the radial direction from the shaft portion 2b, and constitutes an inner peripheral surface facing the plurality of blades 2d. The peripheral wall 4c is opposed to the air blowing side of the blade 2d of the impeller 2. As shown in Fig. 2, the peripheral wall 4c is provided from the scroll start portion 41a located at the boundary with the tongue portion 43, along the rotation direction R of the impeller 2, to the spouting portion 42 on the side away from the tongue portion 43 and Up to the scroll end portion 41b of the boundary of the scroll portion 41. The scroll start portion 41a is the upstream end of the air flow generated by the rotation of the impeller 2 in the peripheral wall 4c constituting the curved surface, and the scroll end 41b is the downstream end of the air flow generated by the rotation of the impeller 2.

The peripheral wall 4c is formed in a spiral shape. The so-called spiral shape refers to a spiral shape based on, for example, an exponential spiral, an Archimedes spiral, or an involute curve. The inner peripheral surface of the peripheral wall 4c is formed from the scroll start portion 41a where the scroll shape starts to the scroll end portion 41b where the scroll shape ends, and is configured to slide along the circumferential direction of the impeller 2. The curved surface that follows the curve. With this structure, the air sent from the impeller 2 flows smoothly in the gap between the impeller 2 and the peripheral wall 4c in the direction of the discharge portion 42. Therefore, in the volute 4, from the tongue portion 43 to the discharge portion 42, the static pressure of the air rises efficiently. Furthermore, the detailed structure of the peripheral wall 4c is described in detail later.

(Discharge part 42) The discharge portion 42 forms a discharge port 42a through which the airflow generated by the impeller 2 and passing through the scroll portion 41 is discharged. The discharge part 42 is formed as a rectangular hollow tube with a cross section orthogonal to the direction of the airflow flowing along the peripheral wall 4c. The discharge part 42 forms a flow path for guiding the air sent from the impeller 2 and flowing in the gap between the peripheral wall 4c and the impeller 2 to the outside of the volute 4.

As shown in FIG. 1, the discharge part 42 is comprised by the extension plate 42b, the diffuser 42c, the 1st side plate 42d, the 2nd side plate 42e, etc. The extension plate 42b is smoothly continuous with the scroll end portion 41b on the downstream side of the peripheral wall 4c so as to be integrally formed with the peripheral wall 4c. The diffuser plate 42c is formed integrally with the tongue 43 of the volute 4 and faces the extension plate 42b. The diffusion plate 42c is formed to have a predetermined angle with the extension plate 42b, so that the cross-sectional area of the flow path gradually expands along the flow direction of the air in the discharge portion 42. The first side plate 42d is integrally formed with the side wall 4a of the volute 4, and the second side plate 42e is integrally formed with the side wall 4a on the opposite side of the volute 4. Furthermore, the first side plate 42d and the second side plate 42e are formed between the extension plate 42b and the diffuser plate 42c. In this way, the discharge part 42 forms a flow path with a rectangular cross section by the extension plate 42b, the diffuser plate 42c, the first side plate 42d, and the second side plate 42e.

(Tongue 43) In the volute 4, a tongue 43 is formed between the diffuser 42c of the discharge portion 42 and the scroll start portion 41a of the peripheral wall 4c. The tongue 43 is formed with a predetermined radius of curvature, and the peripheral wall 4c penetrates the tongue 43 to smoothly connect with the diffuser 42c. The tongue 43 suppresses the inflow of air from the end of the scroll of the scroll-shaped flow path to the start of the scroll. The tongue 43 is provided in the upstream part of the ventilation path, and has the task of dividing the air flow in the rotation direction R of the impeller 2 and the air flow in the discharge direction from the downstream part of the ventilation path to the discharge port 42a. In addition, when the airflow flowing into the discharge portion 42 passes through the volute 4, the static pressure rises and becomes a higher pressure than the inside of the volute 4. Therefore, the tongue 43 has the function of separating this pressure difference.

(Detailed structure of peripheral wall 4c) 3 is a schematic diagram illustrating the relationship between the peripheral wall 4c of the centrifugal fan 1 and the impeller 2 of the first embodiment. 4 is a schematic diagram illustrating the relationship between the peripheral wall 4c and the impeller 2 of the centrifugal fan 1A as a modification of the centrifugal fan 1 of the first embodiment. In addition, in FIGS. 3 and 4, the reference peripheral wall LW shown by the dashed-dotted line represents a general reference peripheral wall that linearly connects the side walls 4a facing each other in a cross section parallel to the axial direction of the rotation axis RS. The position of LW.

The impeller 2 has a main plate 2a, a first blade portion 2d1, and a second blade portion 2d2. The first blade portion 2d1 and the second blade portion 2d2 are composed of a plurality of blades 2d and side plates 2c. More specifically, the first blade portion 2d1 is composed of a ring-shaped first side plate 2c1 arranged opposite to the main plate 2a, and a plurality of blades 2d arranged between the main plate 2a and the first side plate 2c1. The second blade portion 2d2 is composed of a ring-shaped second side plate 2c2 disposed opposite to the main plate 2a on the side opposite to the main plate 2a on the side where the first side plate 2c1 is disposed, and is disposed on the main plate 2a and the second It is composed of a plurality of fan blades 2d between two side plates 2c2. Moreover, the side plate 2c is a general term for the first side plate 2c1 and the second side plate 2c2. The impeller 2 is located in the axial direction of the rotating shaft RS. With respect to the main plate 2a, the side plate 2c1 is provided on one side and the other side The side has a second side plate 2c2.

The first blade portion 2d1 is arranged on the side of the plate surface of one side of the main plate 2a, and the second blade portion 2d2 is arranged on the side of the plate surface of the other side of the main plate 2a. That is, the plurality of blades 2d are arranged on both sides of the main plate 2a in the axial direction of the rotating shaft RS, and the first blade portion 2d1 and the second blade portion 2d2 are set back to back through the main plate 2a. In addition, in FIGS. 3 and 4, the first blade portion 2d1 is arranged above the main plate 2a, and the second blade portion 2d2 is arranged below the main plate 2a. However, the first blade portion 2d1 and the second blade portion 2d2 may be provided back-to-back through the main board 2a. The first blade portion 2d1 may also be arranged below the main board 2a. , Above the main plate 2a, a second blade portion 2d2 is arranged. In addition, in the following description, unless otherwise specified, the blade 2d is described as a general term for the first blade portion 2d1 and the second blade portion 2d2.

The peripheral wall 4c has a first peripheral wall 44a and a second peripheral wall 44b. In the direction orthogonal to the axial direction of the rotating shaft RS of the impeller 2, the first peripheral wall 44a is the peripheral wall 4c opposed to the first blade portion 2d1, and the second peripheral wall 44b is opposed to the second blade portion 2d2周壁4c.

In addition, the peripheral wall 4c has a first raised portion 4c1, a second raised portion 4c2, and a minimum portion 142. The first raised portion 4c1 is formed in the radial direction of the impeller 2 so as to face the first blade portion 2d1, and the second raised portion 4c2 is formed so as to face the second blade portion 2d2. That is, the first raised portion 4c1 is formed on the first peripheral wall 44a, and the second raised portion 4c2 is formed on the second peripheral wall 44b. The minimum portion 142 is in the radial direction of the impeller 2 and is formed so as to face the main plate 2a. In addition, in the following description, the raised portion 4c12 may be referred to as a general term for the first raised portion 4c1 and the second raised portion 4c2. The protruding portion 4c12 is in the rotation direction R of the rotating shaft RS, and only needs to be present in at least a part of the volute 4, or it may be present in the entire area of the volute 4 in the rotating direction R of the rotating shaft RS.

The first raised portion 4c1 is formed such that the distance between the rotation axis RS and the peripheral wall 4c is greater than the distance LS between the rotation axis RS and the reference peripheral wall LW. The first protuberance 4c1 is formed in the axial direction of the rotating shaft RS so that the distance R1 between the rotating shaft RS on the main plate 2a side of the impeller 2 and the peripheral wall 4c is greater than the rotating shaft RS on the side plate 2c side of the impeller 2 and the peripheral wall 4c The distance between R2. The first raised portion 4c1 of the peripheral wall 4c has the first largest portion 141c. The first largest portion 141c is the distance between the first peripheral wall 44a and the rotating shaft RS in a direction orthogonal to the axial direction of the rotating shaft RS of the impeller 2, and becomes the largest first in the axial direction of the rotating shaft RS. Location of peripheral wall 44a. That is, the first largest portion 141c is provided on the peripheral wall 4c of the portion facing the first blade portion 2d1. The first largest portion 141c is located in the axial direction of the rotating shaft RS of the impeller 2, and is formed closer to the main plate 2a side than the intermediate position between the main plate 2a and the first side plate 2c1. That is, the first largest portion 141c is located between the main plate 2a and the first side plate 2c1, and is located at a position up to half the distance from the main plate 2a. In addition, in FIGS. 3 and 4, the distance R1 indicates the distance between the rotation axis RS in the first largest portion 141c and the peripheral wall 4c. The distance R1 between the rotation axis RS in the first largest portion 141c and the peripheral wall 4c is set by the suction air volume of the centrifugal fan 1, and the swelling amount of the first swelling portion 4c1 is set.

Similarly, the second raised portion 4c2 is formed so that the distance between the rotation axis RS and the peripheral wall 4c is greater than the distance LS between the rotation axis RS and the reference peripheral wall LW. The second raised portion 4c2 is formed in the axial direction of the rotating shaft RS. The distance R11 between the rotating shaft RS on the main plate 2a side of the impeller 2 and the peripheral wall 4c is greater than the rotating shaft RS on the side plate 2c side of the impeller 2 and the peripheral wall 4c The distance between R12. The second raised portion 4c2 of the peripheral wall 4c has the second largest portion 141d. The second largest portion 141d is the distance between the second peripheral wall 44b and the rotating shaft RS in a direction orthogonal to the axial direction of the rotating shaft RS of the impeller 2, and becomes the second largest in the axial direction of the rotating shaft RS. Location of peripheral wall 44b. That is, the second largest portion 141d is provided on the peripheral wall 4c of the portion facing the second blade portion 2d2. The second largest portion 141d is located in the axial direction of the rotating shaft RS of the impeller 2, and is formed closer to the main plate 2a than the middle position between the main plate 2a and the second side plate 2c2. That is, the second largest portion 141d is located between the main board 2a and the second side board 2c2, and is located at a position up to half the distance from the main board 2a. In addition, in FIGS. 3 and 4, the distance R11 represents the distance between the rotation axis RS in the second largest portion 141d and the peripheral wall 4c. The distance R11 between the rotating shaft RS and the peripheral wall 4c in the second largest portion 141d is set by the suction air volume of the centrifugal fan 1, and the raised amount of the second raised portion 4c2 is set. In addition, in the following description, the largest portion 141 is referred to as a general term for the first largest portion 141c and the second largest portion 141d.

The minimum portion 142 is in the axial direction of the rotating shaft RS, and is formed between the first raised portion 4c1 and the second raised portion 4c2. The minimum portion 142 is formed such that the distance R13 between the rotation axis RS and the peripheral wall 4c is smaller than the distance R1 and the distance R11 between the rotation axis RS and the peripheral wall 4c in the maximum portion 141. The peripheral wall 4c is located in the axial direction of the rotating shaft RS of the impeller 2 and has a smallest portion 142 between the two largest portions 141. That is, the peripheral wall 4c of the volute 4 is in the axial direction of the rotating shaft RS, and the distance between the peripheral wall 4c and the rotating shaft RS is defined as a position smaller than the position of the first largest part 141c and the second largest part 141d When it is the minimum portion 142, it has the minimum portion 142 at a position opposite to the main board 2a.

The volute 4 is formed as a peripheral wall 4c between the first largest portion 141c and the second largest portion 141d and the smallest portion 142 in the axial direction of the rotating shaft RS, relative to the direction perpendicular to the axial direction of the rotating shaft RS tilt. In addition, the volute 4 is in the axial direction of the rotating shaft RS, and is preferably formed so that the peripheral wall 4c between the first maximum portion 141c and the second maximum portion 141d and the minimum portion 142 is curved. That is, the peripheral wall 4c is a continuous part of the largest part 141 and the smallest part 142, and it is preferable to be formed in an R shape. As shown in FIG. 4, the protrusion amount of the minimum part 142 on the side of the impeller 2 is arbitrary. The volute 4 may be provided with a partition wall 143 extending the wall constituting the minimum portion 142, for example, so that the protrusion amount on the side of the impeller 2 becomes larger. The partition wall 143 is formed so as to partition a part of the space formed by the first raised portion 4c1 and the impeller 2 and a part of the space formed by the second raised portion 4c2 and the impeller 2.

With respect to the side plate 2c side of the impeller 2, the volute 4 has a first raised portion 4c1 and a second raised portion 4c2 to increase the scroll radius on the side of the main plate 2a. The volute 4 has the largest portion 141 with respect to the first blade portion 2d1 and the second blade portion 2d2 by the first raised portion 4c1, the second raised portion 4c2, and the smallest portion 142. That is, the volute 4 is located in the axial direction of the rotating shaft RS, and has two largest portions 141 of a first largest portion 141c and a second largest portion 141d.

5 is a schematic diagram of an example of the relationship between the peripheral wall 4c and the impeller 2 of the centrifugal fan 1 of Embodiment 1 seen from the direction parallel to the axial direction of the rotating shaft RS. 6 is a schematic diagram of another example of the relationship between the peripheral wall 4c and the impeller 2 of the centrifugal fan 1 of Embodiment 1 seen from a direction parallel to the axial direction of the rotating shaft RS. FIG. 7 is a schematic diagram of another example of the relationship between the peripheral wall 4c and the impeller 2 of the centrifugal fan 1 of Embodiment 1 seen from the direction parallel to the axial direction of the rotating shaft RS. Next, using FIGS. 5 to 7, the position and range of the raised portion 4c12 formed in the volute 4 in the rotation direction R of the impeller 2 will be described.

As shown in FIGS. 5 and 6, the raised portion 4c12 may be formed as a part of the volute 4 in the rotation direction R of the impeller 2. That is, the first maximum portion 141c and the second maximum portion 141d are when the boundary with the tongue portion 43 of the divided air flow blown from the impeller 2 is regarded as the scroll start portion 41a, in the rotation direction R of the impeller 2, It is formed as a part from the scroll start portion 41a to the discharge port 42a of the volute 4. When the protruding portion 4c12 is formed as a part of the volute 4, the protruding portion 4c12 is preferably formed next to the suction port of a unit of an air conditioner or the like in which the centrifugal fan 1 is installed. The centrifugal fan 1 and the centrifugal fan 1A are provided with a raised portion 4c12 at a position where the intake amount of air is large, so as to more effectively divide the air described later.

As shown in FIG. 7, the raised portion 4c12 may be continuously formed from the scroll start portion 41a of the volute 4 to the discharge port 42a in the rotation direction R of the impeller 2. In this case, the raised portion 4c12 is provided not only on the scroll portion 41 but also on the discharge portion 42, and the raised portion 4c12 is continuously formed on the peripheral wall 4c and the extension plate 42b. That is, the first maximum portion 141c and the second maximum portion 141d are when the boundary with the tongue portion 43 of the divided air flow blown from the impeller 2 is regarded as the scroll start portion 41a, in the rotation direction R of the impeller 2, It is continuously formed from the scroll start portion 41 a to the discharge port 42 a of the volute 4.

[Operation example of centrifugal fan 1 and centrifugal fan 1A] Fig. 8 is a schematic diagram showing the airflow in the volute 4 of the centrifugal fan 1 of the first embodiment. FIG. 9 is a schematic diagram showing the air flow in the volute 4 of the centrifugal fan 1A as a modification of the centrifugal fan 1 of the first embodiment. In addition, in FIGS. 8 and 9, the solid arrow in the volute 4 represents an example of the flow of wind.

When the impeller 2 rotates, the air outside the volute 4 is sucked into the volute 4 through suction ports 5 formed on both sides of the impeller 2. At this time, the air sucked into the volute 4 is guided by the bell mouth 3 to be sucked by the impeller 2. The air sucked by the impeller 2 is in the process of passing through the plurality of blades 2d, and becomes an air flow with dynamic pressure and static pressure added, and is blown out radially outward of the impeller 2. The air flow blown out from the impeller 2 is trapped in the scroll part 41. When it is guided between the inner side of the peripheral wall 4c and the blade 2d, the dynamic pressure is converted into static pressure, and after passing through the scroll part 41, it is formed in the discharge part. The outlet 42a of 42 is blown out of the volute 4.

[The effect of centrifugal fan 1 and centrifugal fan 1A] The air flow blown out by the rotation of the impeller 2 has a velocity distribution in the direction of the rotation axis RS of the impeller 2, and the air velocity on the side of the main plate 2a becomes larger than the suction port 5 side. According to the present invention, the centrifugal fan 1 and the centrifugal fan 1A have the first largest portion 141c in the axial direction of the rotating shaft RS, which is formed closer to the main plate 2a than the middle position between the main plate 2a and the first side plate 2c1 The second largest portion 141d is in the axial direction of the rotating shaft RS, and is formed closer to the main plate 2a than the middle position between the main plate 2a and the second side plate 2c2. The centrifugal fan 1 and the centrifugal fan 1A have the first largest portion 141c and the second largest portion 141d. The distance between the impeller 2 and the peripheral wall 4c of the volute 4 is wider on the main plate 2a side than the side plate 2c side. Therefore, when the air flowing in from the two suction ports 5 merge on the main plate 2a side, the turbulence of the air flow toward the peripheral wall 4c side is suppressed. Therefore, the centrifugal fan 1 and the centrifugal fan 1A reduce the pressure loss caused by the air flow turbulence, and the air flow can be efficiently boosted in the volute 4.

In addition, when the volute 4 is defined as the smallest portion 142 in the axial direction of the rotating shaft RS, the distance between the peripheral wall 4c and the rotating shaft RS is smaller than the position of the two largest portions 141. The position where 2a faces each other has a minimum portion 142. The centrifugal fan 1 and the centrifugal fan 1A are the airflow on the side of the main board 2a. Because the two largest part 141 and the smallest part 142 are used to smoothly divide the flow, the collision loss generated on the peripheral wall 4c can be reduced. In addition, the air blown from the impeller 2 is discharged by being guided to the discharge port 42a while being boosted by the width of the flow path between the impeller 2 and the peripheral wall 4c. In addition, the centrifugal fan 1 and the centrifugal fan 1A, as shown in FIG. 9, when the partition wall 143 is provided by increasing the protrusion of the minimum portion 142 toward the impeller 2, by double suction, the air flow at the position of the main board 2a can be combined It is more rectified and can boost the airflow efficiently.

In addition, the volute 4 is in the axial direction of the rotating shaft RS, and the peripheral wall 4c between the first largest portion 141c and the second largest portion 141d and the smallest portion 142 is inclined with respect to the direction perpendicular to the axial direction of the rotating shaft RS. . Therefore, when the airflow flowing in from the suction port 5 merges on the side of the main plate 2a, it becomes easy to move from the minimum portion 142 to the two maximum portions 141 side, and the turbulence of the airflow is suppressed. Therefore, the centrifugal fan 1 and the centrifugal fan 1A reduce the pressure loss caused by the air flow turbulence, and the air flow can be efficiently boosted in the volute 4.

In addition, the volute 4 is in the axial direction of the rotating shaft RS, and the peripheral wall 4c between the first maximum portion 141c and the second maximum portion 141d and the minimum portion 142 is curved. Therefore, when the airflow flowing in from the suction port 5 merges on the side of the main plate 2a, it is easy to move from the smallest portion 142 to the two largest portions 141 side, and the turbulence of the airflow is suppressed. In addition, the air flow that merges in the main board 2a becomes easy to flow along the curve of the peripheral wall 4c. Therefore, the centrifugal fan 1 and the centrifugal fan 1A have reduced pressure loss caused by the turbulence of the air flow. In the volute 4, Boost the airflow efficiently.

In addition, the first maximum portion 141 c and the second maximum portion 141 d are formed in a part between the scroll start portion 41 a and the discharge port 42 a of the volute 4 in the rotation direction R of the impeller 2. The centrifugal fan 1 and the centrifugal fan 1A are located in the unit 60, and two largest parts 141 are formed at the place where the intake air volume is large. Thereby, the pressure loss caused by the turbulence of the airflow is further reduced, and the efficiency is good in the volute 4 Ground boost airflow.

In addition, the first maximum portion 141c and the second maximum portion 141d may be continuously formed from the scroll start portion 41a to the discharge port 42a of the volute 4 in the rotation direction R of the impeller 2. The volute 4 of the centrifugal fan 1 and the centrifugal fan 1A is formed with this structure, whereby the centrifugal fan 1 and the centrifugal fan 1A can be assembled into various units 60 even if the places where the intake air volume is large are not specified.

Implementation form 2. 〔Centrifugal fan 1〕 10 is a schematic diagram illustrating the relationship between the peripheral wall 4c and the impeller 2 of the centrifugal fan 1B of the second embodiment. In addition, the same number is assigned to the part having the same structure as the centrifugal fan 1 of FIGS. 1 to 9 and the like, and the description thereof is omitted. The centrifugal fan 1B of the second embodiment has a different shape of the peripheral wall 4c in the centrifugal fan 1 of the first embodiment. Therefore, in the following description, FIG. 10 is used to focus on the structure of the peripheral wall 4c of the centrifugal fan 1B of the second embodiment.

The centrifugal fan 1B is bounded by the main board 2a, and the maximum value of the distance between the impeller 2 and the peripheral wall 4c is different on the side of the two side plates 2c. The peripheral wall 4c has a first raised portion 4c1, a second raised portion 4c22, and a minimum portion 142. The structure of the first raised portion 4c1 is the same as that of the centrifugal fan 1 of the first embodiment.

The second raised portion 4c22 is formed such that the distance between the rotation axis RS and the peripheral wall 4c is greater than the distance LS between the rotation axis RS and the reference peripheral wall LW. The second bulge 4c22 is formed so that in the axial direction of the rotating shaft RS, the distance R111 between the rotating shaft RS on the main plate 2a side of the impeller 2 and the peripheral wall 4c is greater than the rotating shaft RS on the side plate 2c side of the impeller 2 and the peripheral wall The distance between 4c is R112. In addition, the second protruding portion 4c22 is formed such that in the axial direction of the rotating shaft RS, the distance R111 between the rotating shaft RS and the peripheral wall 4c is greater than the distance R1 between the rotating shaft RS of the first protruding portion 4c1 and the peripheral wall 4c. Furthermore, as described above, the distance R1 indicates the distance between the rotation axis RS in the first largest portion 141c and the peripheral wall 4c. That is, in the centrifugal fan 1B of the second embodiment, the sizes of the first raised portion 4c1 and the second raised portion 4c2 are different, and the first distance between the peripheral wall 4c of the second largest portion 141d and the rotating shaft RS is greater than the first largest portion The second distance between the peripheral wall 4c of 141c and the rotation axis RS. In addition, the first distance is a distance R111, and the second distance is a distance R1.

The second raised portion 4c22 of the peripheral wall 4c has a second largest portion 141d in the axial direction of the rotating shaft RS of the impeller 2 where the distance between the rotating shaft RS and the peripheral wall 4c becomes the largest. The second largest portion 141d is provided on the peripheral wall 4c of the portion facing the second blade portion 2d2. The second largest portion 141d is formed in the axial direction of the rotating shaft RS of the impeller 2 and is closer to the main plate 2a side than the middle position between the main plate 2a and the side plate 2c. That is, the second largest portion 141d is located between the main board 2a and the side board 2c, up to a half of the distance from the main board 2a. In addition, in FIG. 10, the distance R111 represents the distance between the rotation axis RS in the second largest portion 141d and the peripheral wall 4c. The distance R111 between the rotating shaft RS and the peripheral wall 4c in the second largest portion 141d is set by the suction air volume of the centrifugal fan 1, and the swelling amount of the second swelling portion 4c22 is set. Furthermore, the positions of the first protruding portion 4c1 and the second protruding portion 4c22 with respect to the main plate 2a may be opposite to the positions of FIG. 10. The second protruding portion 4c22 is provided on the side where the intake amount of air is larger with respect to the main board 2a, whereby the centrifugal fan 1B can more effectively divide the air.

The smallest portion 142 is in the axial direction of the rotating shaft RS, and is formed between the first raised portion 4c1 and the second raised portion 4c22. The minimum portion 142 is formed such that the distance R13 between the rotation axis RS and the peripheral wall 4c is smaller than the distance R1 and the distance R11 between the rotation axis RS and the peripheral wall 4c in the maximum portion 141. That is, the peripheral wall 4c is located in the radial direction of the impeller 2 and has a smallest portion 142 between the two largest portions 141.

11 is a schematic diagram illustrating the relationship between the peripheral wall 4c and the impeller 2 of the centrifugal fan 1C which is a modification of the centrifugal fan 1B of the second embodiment. As shown in FIG. 11, the protrusion amount of the minimum part 142 on the side of the impeller 2 is arbitrary. The volute 4 may be provided with, for example, a partition wall 143 that extends the wall constituting the minimum portion 142, so that the protrusion on the side of the impeller 2 becomes larger. The partition wall 143 is formed so as to partition a part of the space formed by the first raised portion 4c1 and the impeller 2 and a part of the space formed by the second raised portion 4c22 and the impeller 2.

Fig. 12 is a schematic diagram showing the relationship between the centrifugal fan 1C and the resistance body of the important part of the use unit 60. FIG. 13 is an important part of the structure of the use unit 60, showing another schematic diagram of the relationship between the centrifugal fan 1C and the resistance body. 12 and 13 show the centrifugal fan 1C in which the unit 60 is arranged. In addition, the term "unit 60" is a general term for the blower 30, the air conditioner 40, and the like described later. In addition, the wall surface 61 is the wall surface of the casing 7 of the blower 30 described later, or the casing 16 of the air conditioner 40. In addition, in FIG. 12 and FIG. 13, the wall surface 61 and the motor 6 are the resistance bodies of the air flow flowing into the centrifugal fan 1C. The motor 6 is arranged at a position facing the wall surface 61 of the housing 16 and is a resistance body that blocks airflow.

The centrifugal fan 1C has a larger distance between the volute 4 and the resistance body located at a position opposite to the side wall 4a with respect to the main plate 2a, and has a second bulge 4c22. The reason for the formation position of the second protruding portion 4c22 is that the larger the distance between the volute 4 and the resistance body located at the position opposite to the side wall 4a, the suction air volume is larger.

Specifically, when comparing the third distance between the side wall 4a on one side of the volute 4 and the wall surface 61, and the fourth distance between the motor 6 and the side wall 4a on the other side, the second largest portion is arranged at the larger distance In 141d, the first largest portion 141c is arranged at the smaller distance. In other words, when comparing the third distance between the wall surface 61 and the first side wall 4a1 or the second side wall 4a2 facing the wall surface 61, the third distance between the motor 6 and the first side wall 4a1 or the second side wall 4a2 facing the motor 6 In the case of four distances, the second largest portion 141d is arranged for the longer distance, and the first largest portion 141c is arranged for the shorter distance. In addition, the third distance is the distance L1 shown in FIGS. 12 and 13, and the fourth distance is the distance L2 shown in FIGS. 12 and 13. For example, when the volute 4 is the distance L2 between the side wall 4a of the volute 4 and the motor 6 as the resistance body of the air flow, which is greater than the distance L1 between the side wall 4a and the wall surface 61 as the resistance body of the air flow, the motor 6 A second raised portion 4c22 is arranged on the side. In addition, when the volute 4 is the distance L1 between the side wall 4a of the volute 4 and the wall surface 61 as a resistance body for air flow, which is greater than the distance L2 between the side wall 4a and the motor 6 as a resistance body for air flow, The second raised portion 4c22 is arranged on the portion 61 side. In FIGS. 12 and 13, the centrifugal fan 1C is used to illustrate the relationship with the resistance body, but the same effect can be obtained by using the centrifugal fan 1B instead of the centrifugal fan 1C.

[The effect of centrifugal fan 1B and centrifugal fan 1C] 14 is a schematic diagram showing the air flow in the volute 4 of the centrifugal fan 1B of the second embodiment. 15 is a schematic diagram showing the airflow in the volute 4 of the centrifugal fan 1C as a modification of the centrifugal fan 1B of the second embodiment. The air flow blown out by the rotation of the impeller 2 has a speed distribution in the direction of the rotation axis RS of the impeller 2, and the speed of the air flow on the side of the main plate 2a is higher than that of the suction port 5.

As shown in Figs. 14 and 15, the air flow on the side of the main plate 2a is smoothly divided by the first raised portion 4c1, the second raised portion 4c22, and the smallest portion 142. Therefore, the collision loss generated on the peripheral wall 4c can be reduced. . In addition, the air blown from the impeller 2 is tied to the raised portion 4c12, and the width of the flow path between the impeller 2 and the peripheral wall 4c is widened, whereby the air is guided to the discharge port 42a and discharged while the pressure is increased. The centrifugal fan 1B and the centrifugal fan 1C are double-sucked in the same way as the centrifugal fan 1 and the centrifugal fan 1A, and can rectify the air flow that merges at the position of the main board 2a, and can efficiently boost the pressure.

The centrifugal fan 1B and the centrifugal fan 1C are the first distance between the peripheral wall 4c of the second largest portion 141d and the rotating shaft RS, which is greater than the second distance between the peripheral wall 4c of the first largest portion 141c and the rotating shaft RS. Therefore, after the centrifugal fan 1B and the centrifugal fan 1C are assembled into the unit, even if the intake air volume of the suction port 5 of the two is different, the wind speed can be changed to change the distance between the impeller 2 and the peripheral wall 4c, which can boost the pressure more efficiently .

Implementation mode 3. ［Air supply device 30］ Fig. 16 is a diagram showing the structure of the blower 30 of the third embodiment. The parts having the same structure as the centrifugal fan 1 in Figs. 1 to 15 are given the same reference numerals, and their description is omitted. The air blowing device 30 of the third embodiment is, for example, a ventilating fan, a desk fan, and the like. The air blowing device 30 includes a centrifugal fan 1B, a housing 7 for accommodating the centrifugal fan 1B, and a motor 6.

The casing 7 is formed with two openings of a casing suction port 71 through which the gas flowing into the centrifugal fan 1B passes, and a casing discharge port 72 through which the gas blown from the centrifugal fan 1B passes. As shown in FIG. 16, the air blowing device 30 is formed at a position where the casing suction port 71 and the casing discharge port 72 face each other. Furthermore, the air blowing device 30 may be, for example, either the casing suction port 71 or the casing discharge port 72, which is formed above or below the centrifugal fan 1B, and it is not necessarily formed in the casing suction port 71 and the casing discharge port 72 facing each other. position. The housing 7 includes a space SP1 where the housing suction port 71 is formed, and a space SP2 where the housing discharge port 72 is formed, and is partitioned by a partition plate 73. The centrifugal fan 1B is installed in a state where the suction port is located in the space SP1 on the side where the casing suction port 71 is formed, and the discharge port 42a is located in the space SP2 on the side where the casing discharge port 72 is formed.

The motor 6 rotates the impeller 2 of the centrifugal fan 1B. The motor 6 is arranged in a space surrounded by the first blade portion 2d1 of the impeller 2 and the main plate 2a. Therefore, the motor 6 is located in the centrifugal fan 1B and serves as a resistance to the air flow. Therefore, the suction air volume on the second blade portion 2d2 side becomes larger than the suction air volume on the first blade portion 2d1 side. The centrifugal fan 1B is on the side of the second blade portion 2d2 where the intake air volume is large, and is provided with a second raised portion 4c22 having a larger distance between the rotating shaft RS and the peripheral wall 4c than the first raised portion 4c1. In addition, the peripheral wall 4c is formed so that the first largest portion 141c and the second largest portion 141d protrude toward the casing suction port 71.

[Operation example of blower 30] When the air blowing device 30 is driven by the motor 6 and the impeller 2 rotates, air passes through the casing suction port 71 to be sucked into the inside of the casing 7. The air sucked into the inside of the casing 7 is guided by the bell mouth 3 and sucked by the impeller 2. The air sucked in by the impeller 2 is blown out toward the radially outer side of the impeller 2. The air blown out from the impeller 2 passes through the inside of the volute 4 and is blown out from the discharge port 42 a of the volute 4 and blown out from the casing discharge port 72 of the casing 7.

[The effect of the blower 30] The air blowing device 30 is the first distance between the peripheral wall 4c of the second largest portion 141d of the centrifugal fan 1B and the rotating shaft RS, which is greater than the second distance between the peripheral wall 4c of the first largest portion 141c and the rotating shaft RS. Moreover, the motor 6 is arrange|positioned in the space enclosed by the 1st blade part 2d1 and the main board 2a. Therefore, the centrifugal fan 1B of the air blowing device 30, even if the intake air volume of the suction ports 5 on both sides is different due to the presence or absence of the motor 6, it can be adapted to the wind speed, and the distance between the impeller 2 and the peripheral wall 4c can be changed, and it can be lifted more efficiently. Pressure.

In addition, the air blowing device 30 includes a centrifugal fan 1B having a first raised portion 4c1 and a second raised portion 4c22. After the centrifugal fan 1B is assembled in the air blowing device 30, even if the suction air volume of the suction ports 5 on both sides is different, it can be adapted to the wind speed, and the distance between the impeller 2 and the peripheral wall 4c can be changed to boost the pressure more efficiently. The air blowing device 30 includes the centrifugal fan 1B, so the scroll portion 41 can efficiently raise the pressure.

In addition, the peripheral wall 4c of the centrifugal fan 1B constituting the air blowing device 30 is formed such that the first largest portion 141c and the second largest portion 141d protrude toward the casing suction port 71. The centrifugal fan 1B constituting the air blowing device 30 is located in the unit 60, where two largest portions 141 are formed where the intake air volume is large, so that the pressure loss caused by the turbulence of the air flow can be further reduced. , Can boost the airflow efficiently.

In addition, the air blowing device 30 may be arranged outside the volute 4 without disposing the motor 6 to the space surrounded by the first blade portion 2d1. In this case, the air blowing device 30 is constructed so that because of the distance between the side wall 4a and the wall of the housing 7, or the distance between the side wall 4a and the motor 6, the second raised portion 4c22 of the centrifugal fan 1B is located where the suction air volume is larger. side. For example, the centrifugal fan 1B compares the third distance between the side wall 4a on one side of the volute 4 and the wall surface 61, and the fourth distance between the motor 6 and the side wall 4a on the other side. When the third distance and the fourth distance are compared, the second largest portion 141d is arranged in the larger distance, and the first largest portion 141c is arranged in the smaller distance. As a result, the centrifugal fan 1B of the air blowing device 30 can increase the pressure more efficiently by changing the distance between the impeller 2 and the peripheral wall 4c according to the wind speed even if the suction air volume of the two suction ports 5 is different due to the presence or absence of the motor 6.

Furthermore, in the air blowing device 30, when the suction air volume drawn from the suction ports 5 on both sides is substantially the same, the air blowing device 30 can use the centrifugal fan 1 of the first embodiment, etc. That is, the air blowing device 30 is a built-in fan, including any one or more of the centrifugal fan 1, the centrifugal fan 1A, the centrifugal fan 1B, or the centrifugal fan 1C.

Implementation mode 4. [Air Conditioner 40] Fig. 17 is a perspective view schematically showing an example of the air conditioner 40 of the fourth embodiment. Fig. 18 is a schematic diagram showing an example of the internal structure of the air conditioner 40 of the fourth embodiment. Fig. 19 is a side view schematically showing an example of the internal structure of the air conditioner 40 according to the fourth embodiment. Fig. 20 is a side view showing the internal structure of a modification of the air conditioner 40 of the fourth embodiment. In addition, parts having the same structure as the centrifugal fan 1 of FIGS. 1 to 16 are given the same reference numerals, and the description thereof is omitted. In addition, in FIG. 18, in order to show the internal structure of the air conditioner 40, the upper surface part 16a is omitted. The air conditioner 40 of the fourth embodiment includes any one or more of the centrifugal fan 1, the centrifugal fan 1A, the centrifugal fan 1B, or the centrifugal fan 1C, and a heat exchanger arranged at a position facing the discharge port 42a of the centrifugal fan 1, etc. 10. In addition, the air-conditioning apparatus 40 of the fourth embodiment includes a housing 16 installed in the ceiling of the room to be air-conditioned. Furthermore, in the following description, when the centrifugal fan 1 is shown, it is regarded as any one of the centrifugal fan 1, the centrifugal fan 1A, the centrifugal fan 1B, or the centrifugal fan 1C.

(Shell 16) As shown in Fig. 17, the housing 16 is formed in a cube shape including an upper surface portion 16a, a lower surface portion 16b, and a side surface portion 16c. Moreover, the shape of the housing 16 is not limited to a cubic shape, and it may be other shapes such as a cylindrical shape, a square column shape, a conical shape, a shape having a plurality of corners, a shape having a plurality of curved surfaces, and the like. The housing 16 is one of the side parts 16c, and has a side part 16c in which the housing discharge port 17 is formed. The shape of the casing discharge port 17 and the casing suction port 18 is formed in a rectangular shape as shown in FIG. 17. Moreover, the shapes of the casing outlet 17 and casing suction inlet 18 are not limited to rectangular ones, and may be round, elliptical, etc., or other shapes, for example. The housing 16 is located in the side surface portion 16c, and has a side surface portion 16c in which the housing suction port 18 is formed on the inner surface of the surface on which the housing discharge port 17 is formed. A filter for removing dust in the air may be arranged at the casing suction port 18. Furthermore, the casing suction port 18 only needs to be formed at a position perpendicular to the axial direction of the rotating shaft RS of the centrifugal fan 1, and it may be formed with a casing suction port 18a on the lower surface portion 16b shown in FIG. 20, for example. In the case of the air conditioner 40 shown in FIG. 19, the side surface portion 16c is the wall portion of the casing 16 formed by the casing suction port 18. In the case of the air conditioner 40 shown in FIG. 20, the lower surface portion 16b is The wall of the housing 16 in which the housing suction port 18a is formed.

Inside the casing 16, two centrifugal fans 1, a motor 6 and a heat exchanger 10 are housed. The centrifugal fan 1 includes an impeller 2 and a volute 4 formed with a bell mouth 3. The motor 6 is supported by a motor supporter 9 a fixed to the upper surface portion 16 a of the housing 16. The motor 6 has an output shaft 6a. The output shaft 6a is arranged so as to extend in parallel to the surface on which the casing suction port 18 and the casing discharge port 17 are formed in the side surface portion 16c. As shown in FIG. 18, two impellers 2 of the air conditioner 40 are attached to the output shaft 6a. The impeller 2 is drawn into the casing 16 from the casing suction port 18, and forms an air flow that is blown out from the casing discharge port 17 to the air-conditioned space. Moreover, the centrifugal fan 1 arranged in the casing 16 is not limited to two, and it may be one or more than three.

As shown in FIG. 18, the centrifugal fan 1 is installed on the partition plate 19, and the internal space of the housing 16 is partitioned by the partition plate 19 into the suction side space SP11 of the volute 4 and the blowing side of the volute 4. The space SP12.

As shown in FIG. 19, the heat exchanger 10 is arranged at a position facing the discharge port 42a of the centrifugal fan 1, and in the casing 16, it is arranged on the air path of the air discharged from the centrifugal fan 1. The heat exchanger 10 is sucked into the casing 16 from the casing suction port 18, and adjusts the temperature of the air blown out from the casing discharge port 17 to the air-conditioned space. Moreover, the heat exchanger 10 can be applied to a well-known structure.

In the casing 16 of the air conditioner 40, the centrifugal fan 1 is housed so that the bulge 4c12 is arranged on the side with a large amount of suction air. For example, as shown in FIG. 19, the air conditioner 40 has a built-in centrifugal fan 1 such that a bulge 4c12 is arranged on the side of the casing suction port 18. Moreover, as shown in FIG. 20, the air-conditioning apparatus 40 is built with the centrifugal fan 1, so that the protruding part 4c12 is arrange|positioned at the side of the casing suction port 18a. That is, the peripheral wall 4c of the centrifugal fan 1 is formed so that the first largest portion 141c and the second largest portion 141d are raised toward the casing suction port 18 or the casing suction port 18a.

[Operation example of air conditioner 40] When the impeller 2 is driven by the motor 6 to rotate, the air in the air-conditioned space is sucked into the housing 16 through the housing suction port 18 or the housing suction port 18a. The air sucked into the inside of the casing 16 is guided by the bell mouth 3 and sucked by the impeller 2. The air sucked in by the impeller 2 is blown out toward the radially outer side of the impeller 2. The air blown out from the impeller 2 passes through the inside of the volute 4 and then is blown out from the discharge port 42 a of the volute 4 and is supplied to the heat exchanger 10. When the air supplied to the heat exchanger 10 passes through the heat exchanger 10, heat is exchanged, and the temperature and humidity are adjusted. The air that has passed through the heat exchanger 10 is blown out from the casing outlet 17 to the air-conditioned space.

[Effects of Air Conditioner 40] The air conditioner 40 of the fourth embodiment includes the centrifugal fan 1 of the first embodiment and the like. Therefore, the scroll portion 41 can efficiently boost the airflow.

Implementation mode 5. [Refrigeration cycle device 50] Fig. 21 is a diagram showing the structure of a refrigeration cycle apparatus 50 according to the fifth embodiment. In addition, in the indoor fan 202 of the refrigeration cycle apparatus 50 of the fifth embodiment, one or more of the centrifugal fan 1, the centrifugal fan 1A, the centrifugal fan 1B, or the centrifugal fan 1C is used. In addition, in the following description, the refrigerating cycle device 50 is used for air conditioning applications, but the refrigerating cycle device 50 is not limited to those used for air conditioning. The refrigeration cycle device 50 is used for refrigeration applications or air conditioning applications such as refrigerators, freezers, vending machines, air conditioners, refrigeration equipment, and water heaters.

The refrigeration cycle device 50 of the fifth embodiment transmits a refrigerant to transfer heat between the outside air and the indoor air, thereby air-conditioning the indoor heating or cooling room. The refrigeration cycle apparatus 50 of the fifth embodiment includes an outdoor unit 100 and an indoor unit 200. The refrigeration cycle device 50 is the outdoor unit 100 and the indoor unit 200, and is pipe-connected by the refrigerant pipe 300 and the refrigerant pipe 400 to constitute a refrigerant circuit for refrigerant circulation. The refrigerant piping 300 is a gas piping through which a refrigerant in a gas phase flows, and the refrigerant piping 400 is a liquid piping through which a refrigerant in a liquid phase flows. Furthermore, a gas-liquid two-phase refrigerant may flow through the refrigerant pipe 400. Furthermore, in the refrigerant circuit of the refrigeration cycle apparatus 50, the compressor 101, the flow path switching device 102, the outdoor heat exchanger 103, the expansion valve 105, and the indoor heat exchanger 201 are connected in order through refrigerant pipes.

(Outdoor unit 100) The outdoor unit 100 includes a compressor 101, a flow path switching device 102, an outdoor heat exchanger 103, and an expansion valve 105. The compressor 101 compresses the sucked refrigerant to discharge it. The flow path switching device 102 is, for example, a four-way valve, which is a device that switches the direction of the refrigerant flow path. The refrigeration cycle device 50 uses the flow switching device 102 to switch the flow of the refrigerant in accordance with the instruction from the control device 110, thereby enabling heating operation or cooling operation.

The outdoor heat exchanger 103 performs heat exchange between the refrigerant and outdoor air. The outdoor heat exchanger 103 operates the evaporator during heating operation, and exchanges heat between the low-pressure refrigerant flowing in from the refrigerant pipe 400 and outdoor air to evaporate the refrigerant. The outdoor heat exchanger 103 operates the condenser during the cooling operation, and exchanges heat between the refrigerant compressed by the compressor 101 and the outdoor air flowing from the flow switching device 102 side to condense the liquefied refrigerant. In the outdoor heat exchanger 103, in order to improve the efficiency of heat exchange between the refrigerant and outdoor air, an outdoor fan 104 is provided. The outdoor fan 104 can also be equipped with a frequency conversion device to change the operating frequency of the fan motor to change the rotation speed of the fan. The expansion valve 105 is a throttling device (flow control mechanism), which regulates the flow rate of the refrigerant flowing through the expansion valve 105, thereby exerting the function of the expansion valve and adjusting the pressure of the refrigerant by changing the opening degree. For example, when the expansion valve 105 is composed of an electronic expansion valve or the like, it adjusts the opening degree according to the instruction of the control device 110.

(Indoor unit 200) The indoor unit 200 has an indoor heat exchanger 201 for heat exchange between the refrigerant and indoor air, and an indoor fan 202 for adjusting the flow of air for heat exchange in the indoor heat exchanger 201. The indoor heat exchanger 201 operates the condenser during heating operation, exchanges heat between the refrigerant flowing in from the refrigerant pipe 300 and indoor air, condenses the liquefied refrigerant, and flows out to the refrigerant pipe 400 side. The indoor heat exchanger 201 operates the evaporator when the cooling room is running. It exchanges heat between the refrigerant in a low-pressure state caused by the expansion valve 105 and the indoor air. The refrigerant takes the heat of the air to evaporate and gasify it, and flows out to The refrigerant piping 300 side. The indoor fan 202 is arranged to face the indoor heat exchanger 201. As for the indoor fan 202, one or more of the centrifugal fan 1 of Embodiment 1 or the centrifugal fan 1 of Embodiment 2 is applied. The operating speed of the indoor fan 202 is determined by the user's setting. The indoor fan 202 can also be equipped with a frequency conversion device to change the operating frequency of the fan motor (not shown) to change the rotation speed of the impeller 2.

[Operation example of refrigeration cycle device 50] Next, an operation example of the refrigeration cycle device 50 will be described for the cooling operation operation. The high temperature and high pressure gas refrigerant compressed and discharged by the compressor 101 flows into the outdoor heat exchanger 103 via the flow switching device 102. The gas refrigerant that has flowed into the outdoor heat exchanger 103 is condensed by heat exchange with the outside air blown by the outdoor fan 104 to become a low-temperature refrigerant and flows out of the outdoor heat exchanger 103. The refrigerant flowing out of the outdoor heat exchanger 103 is expanded and decompressed by the expansion valve 105 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant. This gas-liquid two-phase refrigerant flows into the indoor heat exchanger 201 of the indoor unit 200, evaporates by heat exchange with the indoor air blown by the indoor fan 202, becomes a low-temperature and low-pressure gas refrigerant, and flows out of the indoor heat exchanger 201. At this time, the indoor air cooled by the heat absorbed by the refrigerant becomes air-conditioned air, and is blown out to the air-conditioned space from the outlet of the indoor unit 200. The gas refrigerant flowing out of the indoor heat exchanger 201 is sucked by the compressor 101 through the flow switching device 102, and is compressed again. The above action is repeated.

Next, an example of the operation of the refrigeration cycle device 50 is to describe the heating operation operation. The high temperature and high pressure gas refrigerant compressed and discharged by the compressor 101 flows into the indoor heat exchanger 201 of the indoor unit 200 via the flow switching device 102. The gas refrigerant flowing into the indoor heat exchanger 201 is condensed by heat exchange with the indoor air blown by the indoor fan 202, becomes a low-temperature refrigerant, and flows out of the indoor heat exchanger 201. At this time, the indoor air heated by receiving heat from the gas refrigerant becomes air-conditioned air, and is blown out to the air-conditioned space from the outlet of the indoor unit 200. The refrigerant flowing out of the indoor heat exchanger 201 is expanded and decompressed by the expansion valve 105 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant. This gas-liquid two-phase refrigerant flows into the outdoor heat exchanger 103 of the outdoor unit 100, and evaporates by heat exchange with the outside air blown by the outdoor fan 104 to become a low-temperature and low-pressure gas refrigerant, and flows out of the outdoor heat exchanger 103 . The gas refrigerant flowing out of the outdoor heat exchanger 103 passes through the flow switching device 102, is sucked by the compressor 101, and is compressed again. The above action is repeated.

The refrigeration cycle device 50 of the fifth embodiment includes the centrifugal fan 1 of the first embodiment and the like, so the scroll portion 41 can efficiently boost the airflow.

The structure shown in the above embodiment is an example, which can be combined with other well-known technologies, and a part of the structure can be omitted or changed within the scope of the essentials.

1: Centrifugal fan 1A: Centrifugal fan 1B: Centrifugal fan 1C: Centrifugal fan 2: impeller 2a: Motherboard 2a1: peripheral part 2b: Shaft 2c: side panel 2c1: 1st side panel 2c2: 2nd side panel 2d: fan blade 2d1: The first fan blade 2d2: The second blade part 2e: suction port 3: Bell mouth 4: Volute 4a: side wall 4a1: 1st side wall 4a2: second side wall 4c: peripheral wall 4c1: 1st bulge 4c121: Uplift 4c2: 2nd bulge 4c22: 2nd bulge 5: suction port 5a: The first suction port 5b: The second suction port 6: Motor 6a: output shaft 7: Shell 9a: Motor support 10: Heat exchanger 16: shell 16a: Upper surface part 16b: Lower face 16c: side 17: Shell spout 18: Shell suction port 18a: Shell suction port 19: divider 30: Air supply device 40: Air Conditioner 41: Scroll 41a: Scroll start 41b: End of scroll 42: Discharge part 42a: spit out 42b: Extension board 42c: diffuser 42d: 1st side panel 42e: 2nd side panel 43: Tongue 44a: Week 1 wall 44b: Week 2 wall 50: refrigeration cycle device 60: unit 61: wall face 71: Shell suction port 72: shell spout 73: divider 100: outdoor unit 101: Compressor 102: Flow switching device 103: outdoor heat exchanger 104: outdoor fan 105: Expansion valve 110: control device 141: largest part 141c: The first largest part 141d: the second largest part 142: The smallest part 143: Partition Wall 200: indoor unit 201: Indoor heat exchanger 202: Indoor fan 300: refrigerant piping 400: refrigerant piping

[Figure 1] is a perspective view of the centrifugal fan in Embodiment 1; [Figure 2] is a schematic diagram showing the relationship between the impeller and the peripheral wall of the volute in Figure 1; [Figure 3] is a schematic diagram illustrating the relationship between the peripheral wall of the centrifugal fan and the impeller in Embodiment 1; [Figure 4] is a schematic diagram illustrating the relationship between the peripheral wall of the centrifugal fan and the impeller as a modification of the centrifugal fan of the first embodiment; [Figure 5] is a schematic diagram of an example of the relationship between the peripheral wall of the centrifugal fan and the impeller of Embodiment 1 seen from the direction parallel to the axial direction of the rotating shaft; [Figure 6] is a schematic diagram of another example of the relationship between the peripheral wall of the centrifugal fan and the impeller in Embodiment 1 seen from the direction parallel to the axial direction of the rotating shaft; [Figure 7] is a schematic diagram of another example of the relationship between the peripheral wall of the centrifugal fan and the impeller in Embodiment 1 seen from the direction parallel to the axial direction of the rotating shaft; [Figure 8] is a schematic diagram showing the airflow in the volute of the centrifugal fan in the first embodiment; [Fig. 9] is a schematic diagram showing the airflow in the volute of the centrifugal fan as a modification of the centrifugal fan in the first embodiment; [Figure 10] is a schematic diagram illustrating the relationship between the peripheral wall of the centrifugal fan and the impeller in the second embodiment; [Figure 11] is a schematic diagram illustrating the relationship between the peripheral wall of the centrifugal fan and the impeller as a modification of the centrifugal fan of the second embodiment; [Figure 12] is an important part of the structure of the use unit, a schematic diagram showing the relationship between the centrifugal fan and the resistance body; [Figure 13] is an important part of the structure of the use unit, another schematic diagram showing the relationship between the centrifugal fan and the resistance body; [Figure 14] is a schematic diagram showing the airflow in the volute of the centrifugal fan in the second embodiment; [FIG. 15] is a schematic diagram showing the airflow in the volute of the centrifugal fan as a modification of the centrifugal fan of the second embodiment; [Figure 16] is a diagram showing the structure of the blower in the third embodiment; [Fig. 17] is a perspective view schematically showing an example of the air conditioner of Embodiment 4; [FIG. 18] is a schematic diagram showing an example of the internal structure of the air conditioner in Embodiment 4; [Figure 19] is a side view schematically showing an example of the internal structure of the air conditioner in Embodiment 4; [Figure 20] is a side view showing the internal structure of a modified example of the air conditioner of Embodiment 4; and [Fig. 21] is a diagram showing the structure of the refrigeration cycle apparatus of the fifth embodiment.

1: Centrifugal fan

2: impeller

2a: Motherboard

2c1: 1st side panel

2c2: 2nd side panel

2d1: The first fan blade

2d2: The second blade part

3: Bell mouth

4: Volute

4a1: 1st side wall

4a2: second side wall

4c: peripheral wall

4c1: 1st bulge

4c2: 2nd bulge

5a: The first suction port

5b: The second suction port

44a: Week 1 wall

44b: Week 2 wall

141: largest part

141c: The first largest part

141d: The second largest part

142: The smallest part

R1: distance

R2: distance

R11: distance

R12: distance

R13: distance

LS: distance

LW: reference wall

RS: Rotating axis

Claims (14)

A centrifugal fan, which includes an impeller and a volute, The impeller system has: a main plate which is rotatably driven; a first blade portion composed of a ring-shaped first side plate arranged opposite to the main plate and a plurality of blades arranged between the main plate and the first side plate; and The 2 blade section consists of a ring-shaped second side plate disposed opposite to the main plate on the side opposite to the side where the first side plate is disposed with respect to the main plate, and is disposed between the main plate and the second side plate Composed of plural fan blades, The volute system has: a peripheral wall formed in a spiral shape; a first side wall formed with a first suction port facing the plate surface of the main plate on the side where the first side plate is arranged; and a second side wall formed with The second suction port on the plate surface of the main plate facing the side where the second side plate is arranged; accommodating the impeller, When the peripheral wall facing the first blade portion is defined as the first peripheral wall, the peripheral wall facing the second blade portion is defined as the second peripheral wall, The distance between the first peripheral wall and the rotating shaft in a direction orthogonal to the axial direction of the rotating shaft of the impeller is defined as the position of the first peripheral wall that becomes the largest in the axial direction. 1 largest part, When the distance between the second peripheral wall and the rotating shaft in a direction orthogonal to the axial direction is the position of the second peripheral wall that becomes the largest in the axial direction, and is defined as the second largest portion, The first largest part is formed in the axial direction, and is closer to the main plate side than the intermediate position between the main plate and the first side plate, and the second largest part is formed in the axial direction, which is shorter than the intermediate position between the main plate and the The middle position between the second side plates is also formed close to the aforementioned main board side. The centrifugal fan described in claim 1, wherein, in the peripheral wall, the distance between the peripheral wall and the rotating shaft becomes larger than the positions of the first largest part and the second largest part The small position is defined as the smallest part, The peripheral wall is located at a position opposite to the main board, and has the minimum portion. The centrifugal fan described in item 2 of the scope of patent application, wherein the aforementioned volute is The peripheral wall between the first largest portion, the second largest portion and the smallest portion is inclined with respect to a direction perpendicular to the axial direction. The centrifugal fan described in item 3 of the scope of patent application, wherein the aforementioned volute is The peripheral wall between the first largest portion, the second largest portion and the smallest portion is curved. The centrifugal fan described in any one of items 1 to 4 in the scope of the patent application, wherein the first largest part and the second largest part are When the boundary with the tongue portion of the airflow that is divided from the impeller is regarded as the start of the scroll, it is formed from the start of the scroll to the outlet of the volute in the direction of rotation of the impeller. Part of the room. The centrifugal fan described in any one of items 1 to 4 in the scope of the patent application, wherein the first largest part and the second largest part are When the boundary with the tongue part of the divided air flow blown from the impeller is regarded as the start of the scroll, it is continuously formed from the start of the scroll to the outlet of the volute in the direction of rotation of the impeller. between. The centrifugal fan according to any one of items 1 to 4 in the scope of the patent application, wherein the first distance between the second largest part and the rotating shaft is greater than the distance between the first largest part and the rotating shaft The second distance. The centrifugal fan described in item 7 of the scope of patent application, which further includes a motor that rotates the aforementioned motherboard, The motor is arranged in a space surrounded by the first fan portion and the main plate. An air supply device, which includes: Centrifugal fans, those mentioned in any one of items 1 to 8 of the scope of patent application; and The casing for containing the aforementioned centrifugal fan An air supply device, which includes: Centrifugal fan, as mentioned in item 7 of the scope of patent application; A housing containing the aforementioned centrifugal fan; and The resistance body is arranged at a position opposite to the wall surface of the aforementioned housing to obstruct the flow of air, The aforementioned centrifugal fan has the aforementioned volute, For the volute, compare the third distance between the wall surface and the first side wall or the second side wall facing the wall surface, and the resistance body and the first side wall or the second side wall facing the resistance body. In the case of the fourth distance between the side walls, the second largest part is arranged at the larger distance, and the first largest part is arranged at the smaller distance. The air blowing device described in item 9 or 10 of the scope of patent application, wherein the housing is formed with a housing suction port through which the gas flowing into the centrifugal fan passes, The peripheral wall is formed so that the first largest portion and the second largest portion bulge toward the casing suction port. An air conditioner, which includes: Centrifugal fans, those mentioned in any one of items 1 to 8 of the scope of patent application; and The heat exchanger is arranged at a position facing the outlet of the centrifugal fan. The air conditioner described in claim 12, which further includes a housing that houses the centrifugal fan and the heat exchanger, and has a wall formed with a housing suction port through which the gas flowing into the centrifugal fan passes, The peripheral wall is formed so that the first largest portion and the second largest portion bulge toward the casing suction port. A refrigerating cycle device comprising the centrifugal fan described in any one of items 1 to 8 of the scope of patent application.

Images