Patent Application
20210033104
The present invention relates to a centrifugal air blower having a scroll casing, and an air-blowing apparatus, an air-conditioning apparatus, and a refrigeration cycle apparatus that include the centrifugal air blower.
A scroll casing of a centrifugal air blower has a bell mouth that guides an airflow sucked into a suction opening. If the axial distance between the upstream end and the downstream end of the bell mouth is short in the centrifugal air blower, the direction of the airflow changes suddenly, and turbulence occurs in the flow, resulting in a decrease in air blowing efficiency. Patent Literature 1 discloses a centrifugal air blower in which at least the portion of the bell mouth of the scroll casing having a higher air inflow velocity protrudes outward from the scroll casing.
In the invention disclosed in Patent Literature 1, the axial distance between the upstream end and the downstream end of the bell mouth is partially long, and accordingly, the airflow is gradually changed at the suction opening. Thus, turbulence hardly occurs in the flow, and the decrease in air blowing efficiency can be effectively reduced.
Patent Literature 1: Japanese Patent Application Laid-open No. 5-17400
In the invention disclosed in Patent Literature 1, however, the bell mouth is not widened in the radial direction, and therefore, there is room for improvement of the air blowing efficiency.
The present invention has been made in view of the above, and aims to obtain a centrifugal air blower with enhanced air blowing efficiency.
To solve the above problem and achieve the object, a centrifugal air blower according to the present invention comprises: a fan including a disk-shaped main plate and a plurality of blades disposed on a peripheral portion of the main plate; and a scroll casing. The scroll casing includes: a sidewall covering the fan from an axial direction of a rotation axis on which the fan rotates, the side wall having a suction opening for sucking air; a discharge opening for discharging an airflow generated by the fan; a tongue portion for guiding the airflow to the discharge opening; a peripheral wall surrounding the fan from a radial direction of the rotation axis; and a bell mouth formed along the suction opening of the sidewall. The bell mouth includes an upstream end and a downstream end, the upstream end being an end portion on an upstream side in a direction of flow of the air passing through the suction opening, the downstream end being an end portion on a downstream side in the direction of flow of the air. A distance in the radial direction of the rotation shaft between the upstream end and the downstream end at a location larger than the tongue portion in angle of a direction of rotation of the fan is longer than a distance in the radial direction between the upstream end and the downstream end at a location adjacent to the tongue portion.
A centrifugal air blower according to the present invention has an effect of enhancing the air blowing efficiency.
The following is a detailed description of a centrifugal air blower, an air-blowing apparatus, an air-conditioning apparatus, and a refrigeration cycle apparatus according to embodiments of the present invention, with reference to the drawings. Note that the present invention is not limited by the embodiments.
The fan 2 includes a disk-shaped main plate 2a, a ring-shaped side plate 2c facing the main plate 2a, and a plurality of blades 2d disposed at the peripheral portion of the main plate 2a. The blades 2d surround a rotation axis AX between the main plate 2a and the side plate 2c. The main plate 2a has its central portion providing a boss portion 2b. An output shaft 6a of a fan motor 6 is connected to the center of the boss portion 2b, and the fan 2 is rotated by the driving force of the fan motor 6. Note that the fan 2 may have a structure without the side plate 2c.
The scroll casing 4 surrounds the fan 2, and rectifies the air blown from the fan 2. The scroll casing 4 includes a sidewall 4c, a peripheral wall 4a, a discharge opening 41, and a tongue portion 4b. The sidewall 4c covers the fan 2 from the axial direction of the rotation axis AX. The peripheral wall 4a covers the fan 2 from the radial direction of the rotation axis AX. The discharge opening 41 discharges an airflow generated by the fan 2. The tongue portion 4b guides the airflow generated by the fan 2 to the discharge opening 41. Note that the radial direction of the rotation axis AX is a direction perpendicular to the rotation axis AX. The inside of a scroll portion 4e defined by the peripheral wall 4a and the sidewall 4c is a space in which air blown from the fan 2 flows along the peripheral wall 4a.
The discharge opening 41 has an end portion 41a located on the side of the tongue portion 4b, and an end portion 41b located on the side away from the tongue portion 4b. The peripheral wall 4a extends from the end portion 41a to the end portion 41b in the direction of rotation of the fan 2. Accordingly, the scroll portion 4e is contiguous with the discharge opening 41 without the peripheral wall 4a being provided therebetween. A distance between the rotation axis AX of the fan 2 and the peripheral wall 4a becomes longer as an angle θ relative to the tongue portion 4b in the direction of rotation of the fan 2 increases between the tongue portion 4b and a location at which the peripheral wall 4a is contiguous with the discharge opening 41. The distance between the rotation axis AX of the fan 2 and the peripheral wall 4a is shortest at the end portion 41a.
A suction opening 5 is formed in the sidewall 4c of the scroll casing 4. The sidewall 4c defines the bell mouth 3. An airflow to be sucked into the scroll casing 4 through the suction opening 5 is guided by the bell mouth 3. The bell mouth 3 is formed at a position at which the fan 2 faces the suction opening 5. The bell mouth 3 has an upstream end 3a and a downstream end 3b. The upstream end 3a is an end on an upstream side of an airflow to be sucked into the scroll casing 4 through the suction opening 5, and the downstream end 3b is an end on a downstream side of the airflow. The bell mouth 3 is shaped to provide an airflow path narrowing from the upstream end 3a toward the downstream end 3b. In the air blower 1 according to the first embodiment, the bell mouth 3 has a curved surface having a curved cross-sectional shape in the plane including the rotation axis AX. However, the bell mouth 3 may have a curved surface having a linear cross-sectional shape in the plane including the rotation axis AX. In other words, the bell mouth 3 may be like the side face of a circular truncated cone.
The peripheral portion of the bell mouth 3 has a curved portion 31 having a curved surface convex in a direction away from the main plate 2a, and smoothly connects the bell mouth 3 and the peripheral wall 4a of the scroll casing 4. Here, the phrase “smoothly” means that the tilting of the curved surface continuously changes between the bell mouth 3 and the peripheral wall 4a, such that any edge is not formed at the boundary between the bell mouth 3 and the peripheral wall 4a.
A step 42 is formed at the boundary between the discharge opening 41 and the scroll portion 4e, such that the airflow is reduced in the cross-sectional area as the air flow travels from the scroll portion 4e toward the discharge opening 41. Since the cross-sectional area of the airflow that travels from the scroll portion 4e toward the discharge opening 41 is reduced, the flow rate of the airflow blown out of the scroll casing 4 through the discharge opening 41 becomes higher.
A radial distance between the upstream end 3a and the downstream end 3b of the bell mouth 3 is longer at a location where an angle relative to the end portion 41a in the direction of rotation of the fan 2 is larger between the end portion 41a and the end portion 41b.
Lθ represents the radial distance between the upstream end 3a and the downstream end 3b of the bell mouth 3 at a location where an angle relative to the end portion 41a in the direction of rotation of the fan 2 is θ degrees. L0 can be defined as the distance between the upstream end 3a and the downstream end 3b on the line segment interconnecting the end portion 41a and the rotation axis AX as viewed from above. Further, L270 can be defined as the distance between the upstream end 3a and the downstream end 3b on the line segment interconnecting the end portion 41b and the rotation axis AX as viewed from above. In the air blower 1 according to the first embodiment, L90 is longer than L0, and L180 is longer than L90. The radial distance L between the upstream end 3a and the downstream end 3b of the bell mouth 3 becomes longest at L270 where the scroll casing 4 is connected to the discharge opening 41, after which the radial distance L becomes shortest at L360 corresponding to the end portion 41a. For example, the radial distance Lθ between the upstream end 3a and the downstream end 3b of the bell mouth 3 becomes longer as the angle θ increases in the range of 0 degrees to 270 degrees. The radial distance Lθ between the upstream end 3a and the downstream end 3b of the bell mouth 3 may continuously become longer from the end portion 41a toward the end portion 41b, or may become longer stepwise. Note that the angle at which the radial distance between the upstream end 3a and the downstream end 3b of the bell mouth 3 becomes longest may be any angle between 0 degrees and 360 degrees, and is not limited to 270 degrees as illustrated as an example. In other words, the radial distance between the upstream end 3a and the downstream end 3b of the bell mouth 3 may become longest at a location where the angle relative to the end portion 41a in the direction of rotation of the fan 2 is between 0 degrees and 360 degrees, and may become gradually shorter in the direction of the rotation of the fan 2.
Here, the peripheral wall 4a is continuous with the discharge opening 41 at a location where the angle relative to the end portion 41a in the direction of rotation of the fan 2 is 270 degrees. However, the peripheral wall 4a may be contiguous with the discharge opening 41 at a location where the angle relative to the end portion 41a is any angle other than 270 degrees.
When the fan 2 rotates, the air outside the scroll casing 4 is sucked into the scroll casing 4 through the suction opening 5. The air sucked into the scroll casing 4 is guided by the bell mouth 3 and is sucked into the fan 2. The air sucked into the fan 2 is blown out of the fan 2 in the radial direction toward the outside. The air blown out of the fan 2 passes through the scroll portion 4e, and is then blown out of the scroll casing 4 through the discharge opening 41.
Since the distance between the upstream end 3a and the downstream end 3b of the bell mouth 3 at any location other than the end portion 41a is longer than the distance between the upstream end 3a and the downstream end 3b at the end portion 41a, the airflow sucked into the scroll casing 4 through the suction opening 5 is not easily separated from the bell mouth 3. Thus, the air blower 1 according to the first embodiment can reduce the decrease in air blowing efficiency, and reduce noise.
In the air blower 1 according to the first embodiment, the bell mouth 3 and the peripheral wall 4a of the scroll casing 4 are smoothly connected to each other by the curved portion 31. Thus, the air on the side of the peripheral wall 4a flows along the curved portion 31, and is guided to the bell mouth 3. Since the boundary portion between the bell mouth 3 and the peripheral wall 4a of the scroll casing 4 is defined by the curved portion 31, air blowing efficiency is enhanced.
In the air blower 1 according to the first modification of the first embodiment, at least one of the engaging portions 44 that join the components of the bell mouth 3 is disposed between the upstream end 3a of the bell mouth 3 and the peripheral wall 4a of the scroll casing 4 and closer to the main plate 2a in the axial direction of the rotation axis AX than the upstream end 3a. Accordingly, it is less likely that the airflow sucked into the scroll casing 4 through the suction opening 5 is hindered by the engaging portion 44. Thus, the air blower 1 according to the first modification can achieve a higher air blowing efficiency than an air blower that has all the engaging portions disposed between the upstream end of the bell mouth and the suction opening.
As described above, in the air blower 1 according to the first embodiment, the radial distance between the upstream end 3a and the downstream end 3b of the bell mouth 3 increases in the direction of rotation of the fan 2 from the radial distance between the upstream end 3a and the downstream end 3b at the end portion 41a. As a result, separation of the flow in the bell mouth 3 can be reduced or prevented. Thus, the air blower 1 according to the first embodiment can achieve a higher efficiency and reduce noise by reducing or preventing the separation of the flow in the bell mouth 3.
Note that the bell mouth 3 does not necessarily reach the peripheral wall 4a of the scroll casing 4 at any portion other than the end portion 41a.
Modifications 3 through 7 described above can be combined. For example, providing at least one of the curling start portion of the scroll casing 4, the curling end portion of the scroll casing 4, and the location opposite to the tongue portion 4b with the flat surface portion 45 or the curved surface portion 46 can reduce noise. Further, the curling start portion of the scroll casing 4 may be provided with the curved surface portion 46, as well as the engaging portion 44 being provided closer to the main plate 2a than the upstream end 3a in the axial direction of the rotation axis AX and between the upstream end 3a of the bell mouth 3 and the peripheral wall 4a of the scroll casing 4.
In the air blower 1 according to the second embodiment, the curvature of the bell mouth 3 from the upstream end 3a to the downstream end 3b is smaller than that the curvature of the bell mouth providing an arc-shaped cross-section where A=B. As a result, the air blower 1 according to the second embodiment provides the greater effect of making it separation of the suction airflow from the bell mouth 3 unlikely than an air blower with the bell mouth having the arc-shaped cross-section where A=B.
In a case where the distance B is longer than the distance A, the curvature of the bell mouth 3 from the upstream end 3a to the downstream end 3b is smaller than the curvature of the bell mouth providing the arc-shaped cross-section where the distance A=the distance B. Also, the suction airflow is changed by the axial direction of the rotation axis AX in the bell mouth 3 from the upstream end 3a to the downstream end 3b, and thus, an airflow that is uniform in the axial direction can be sent into the fan 2. As a result, the air blower 1 according to the third embodiment provides an increased power of the fan 2 in the axial direction of the rotation axis AX. Thus, it is possible to achieve a higher efficiency, and reduce noise.
The air blower 1 according to the fourth embodiment has a lower air blowing efficiency than that of the air blower 1 according to the first embodiment having the curved portion 31 formed at the boundary between the peripheral wall 4a and the bell mouth 3. However, the air blower 1 according to the fourth embodiment achieves a high efficiency and reduces noise as compared to an air blower designed such that the radial distance between the upstream end 3a and the downstream end 3b of the bell mouth 3 is uniform regardless of the angle relative to the end portion 41a in the direction of rotation of the fan 2.
In the air blower 1 according to the fifth embodiment, the airflow generated by the fan 2 does not receive resistance due to passing through the step within the scroll portion 4e as the airflow travels from the scroll portion 4e to the discharge opening 41. Thus, air blowing efficiency can be enhanced.
As the air blower 1 according to the sixth embodiment can also reduce or prevent separation of the flow at the suction opening 5 in the axial direction, the air blower 1 according to the sixth embodiment can achieve a higher efficiency and reduce noise more effectively than the air blower 1 according to the first embodiment.
When the air blower 1 according to the sixth embodiment is housed in a case having a case suction opening oppositely to the discharge opening 41, the upstream end 3a of the bell mouth 3 is located far away from the main plate 2a on the side of the case suction opening. Accordingly, the curvature of the bell mouth 3 can be smaller. Thus, the air blower 1 according to the sixth embodiment can reduce separation of the airflow in the bell mouth 3, and enhance air blowing efficiency.
When the air blower 1 according to the seventh embodiment is housed in a case having a case suction opening oppositely to the discharge opening 41, the upstream end 3a of the bell mouth 3 is located far away from the main plate 2a on the side of the case suction opening, as in the air blower 1 according to the sixth embodiment. Accordingly, the curvature of the bell mouth 3 can be smaller. Thus, the air blower 1 according to the seventh embodiment can reduce separation of the airflow in the bell mouth 3, and enhance air blowing efficiency.
When the air blower 1 according to the eighth embodiment is housed in a case having a case suction opening oppositely to the discharge opening 41, the upstream end 3a of the bell mouth 3 is located close to the main plate 2a on the side of the case suction opening. Accordingly, a wide airflow path can be secured between the air blower 1 and the case housing the air blower 1. Thus, the air blower 1 according to the eighth embodiment can enhance air blowing efficiency. Further, in the air blower 1 according to the eighth embodiment, the upstream end 3a of the bell mouth 3 is located far away from the main plate 2a on the side of the discharge opening 41 and the end portion 41a, and the curvature in the axial direction of the bell mouth 3 is smaller. As a result, the noise increase due to standing waves can be reduced.
When the air blower 1 according to the ninth embodiment is housed in a case having a case suction opening oppositely to the discharge opening 41, the upstream end 3a of the bell mouth 3 is located close to the main plate 2a on the side of the case suction opening. Accordingly, a wide airflow path can be secured between the air blower 1 and the case housing the air blower 1. Thus, the air blower 1 according to the ninth embodiment can enhance air blowing efficiency.
The air-blowing apparatus 30 according to the tenth embodiment includes the air blower 1 in which the radial distance between the upstream end 3a and the downstream end 3b of the bell mouth 3 becomes longer in the direction of rotation of the fan 2 than the distance in the radial direction at the end portion 41a of the discharge opening 41. Thus, a higher air blowing efficiency can be achieved, and noise can be reduced. Further, since the portion providing the longest radial distance A1 between the upstream end 3a and the downstream end 3b is disposed on the side of the case suction opening 71, the fast airflow entering from the case suction opening 71 can be smoothly guided along the bell mouth 3. Accordingly, separation of the airflow from the bell mouth 3 can be reduced. Thus, air blowing efficiency can be enhanced, and noise can be reduced. Note that the same effects as above can be achieved in a case where the air-blowing apparatus 30 includes an air blower 1 according to one of the second through ninth embodiments.
A case discharge opening 17 is formed in one of the side surface portions 16c of the case 16. The shape of the case discharge opening 17 is not limited to any particular shape. The shape of the case discharge opening 17 may be rectangular, for example. Of the side surface portions 16c of the case 16, a surface opposite to the surface having the case discharge opening 17 formed therein has a case suction opening 18 formed therein. The shape of the case suction opening 18 is not limited to any particular shape. The shape of the case suction opening 18 may be rectangular, for example. A filter for removing dust in the air may also be disposed in the case suction opening 18.
The case 16 houses two air blowers 11, a fan motor 9, and a heat exchanger 10. The air blowers 11 each include a scroll casing 4 defining a bell mouth 3 and a fan 2. Each air blower 11 has the same fan 2 and the same scroll casing 4 as those of the air blower 1 according to the first embodiment, but differs from the air blower 1 in that the fan motor 6 is not disposed in the scroll casing 4. Accordingly, the shape of the bell mouth 3 of each air blower 11 is the same as that of the first embodiment. The fan motor 9 is supported by a motor support 9a secured to the upper surface portion 16a of the case 16. The fan motor 9 has a rotation axis AX. The two surfaces among the side surface portions 16c have the case discharge opening 17 and the case suction opening 18 formed therein respectively, and the rotation axis AX is positioned extending in parallel to these two surfaces. In the air-conditioning apparatus 40 illustrated in
The heat exchanger 10 is disposed in the airflow path. The heat exchanger 10 adjusts the temperature of the air. Note that a heat exchange having a known structure may be used as the heat exchanger 10.
The space on the suction side of the scroll casing 4 and the space on the discharge side are separated by a partition plate 19.
When the fans 2 rotate, the air in the room to be air-conditioned is sucked into the case 16 through the case suction opening 18. The air sucked into the case 16 is guided to the bell mouths 3 and is sucked into the fans 2. The air sucked into the fans 2 is blown radially outward. The air blown out of the fans 2 passes through the inside of the scroll casing 4, is blown out from the discharge opening 41 of each scroll casing 4, and is supplied to the heat exchanger 10. The air supplied to the heat exchanger 10 is subjected to heat exchange and humidity adjustment, while passing through the heat exchanger 10. The air that has passed through the heat exchanger 10 is blown out from the case discharge opening 17 into the room.
In the air-conditioning apparatus 40 according to the eleventh embodiment, the airflow sucked into the air blowers 11 is unlikely to be separated from the bell mouth 3. Thus, air blowing efficiency can be enhanced, and noise can be reduced.
Note that, in the above description, the shape of the bell mouth 3 of each air blower 11 is the same as that of the air blower 1 according to the first embodiment. However, the shape of the bell mouth 3 of each air blower 11 may be the same as the shape of the bell mouth 3 of the air blower 1 according to one of the second through ninth embodiments. Also, each air blower 11 may be installed such that a portion of the bell mouth 3 providing the longest radial distance A1 between the upstream end 3a and the downstream end 3b of the bell mouth 3 in the entire circumference of the bell mouth 3 is located on the side of the case suction opening 18, as in the air-blowing apparatus 30 according to the tenth embodiment.
The outdoor unit 100 includes a compressor 101, a four-way valve 102, an outdoor heat exchanger 103, an outdoor air blower 104, and a throttle device 105.
The compressor 101 compresses a sucked refrigerant, and discharges the compressed refrigerant. Here, the compressor 101 includes an inverter device, and it is possible to change the capacity of the compressor 101 by changing the operation frequency. Note that the capacity of the compressor 101 is the amount of the refrigerant to be sent out per unit time. The four-way valve 102 switches the flow of the refrigerant between a cooling operation and a heating operation, in accordance with an instruction from a control device (not shown).
The outdoor heat exchanger 103 conducts heat exchange between the refrigerant and the outdoor air. The outdoor heat exchanger 103 functions as an evaporator during a heating operation, and conducts heat exchange between the outdoor air and the low-pressure refrigerant having entered through the liquid pipe 400, to evaporate and vaporize the refrigerant. The outdoor heat exchanger 103 functions as a condenser during a cooling operation, and conducts heat exchange between the outdoor air and the refrigerant that has entered from the side of the four-way valve 102 and been compressed by the compressor 101, to condense and liquefy the refrigerant.
The outdoor heat exchanger 103 is provided with the outdoor air blower 104, to enhance the efficiency of heat exchange between the refrigerant and the outdoor air. The outdoor air blower 104 may change the operation frequency of the fan motor 6 with the inverter device, to change the rotation speed of the fan 2. The throttle device 105 changes the size of the opening, to adjust the pressure of the refrigerant.
The indoor unit 200 includes a load heat exchanger 201 that conducts heat exchange between the refrigerant and the indoor air, and a load air blower 202 that adjusts the flow of the air in which the load heat exchanger 201 conducts heat exchange. The load heat exchanger 201 functions as a condenser during a heating operation, conducts heat exchange between the indoor air and the refrigerant having entered through the gas pipe 300, condenses and liquefies the refrigerant, and lets the refrigerant flow out to the liquid pipe 400. The load heat exchanger 201 functions as an evaporator during a cooling operation, conducts heat exchange between the indoor air and the refrigerant put into a low-pressure state by the throttle device 105, lets the refrigerant remove heat from the air to evaporate and liquefy the refrigerant, and lets the refrigerant flow out to the gas pipe 300. The operation speed of the load air blower 202 is determined by a user setting.
The refrigeration cycle apparatus 50 according to the twelfth embodiment moves heat between outdoor air and indoor air via a refrigerant, and thus, heats or cools a room to perform air conditioning.
In the refrigeration cycle apparatus 50 according to the twelfth embodiment, an air blower 1 according to one of the first through ninth embodiments is used as the outdoor air blower 104, to reduce air volume and noise.
Note that the load air blower 202 of the indoor unit 200 may include a bell mouth 3 having the same shape as that of an air blower 1 according to one of the first through ninth embodiments.
The configurations described in the above embodiments are examples of the subject matter of the present invention, and can be combined with other known techniques, or may be partially omitted or modified without departing from the scope of the present invention.
1, 11 air blower; 2 fan; 2a main plate; 2b boss portion; 2c side plate; 2d blade; 3 bell mouth; 3a upstream end; 3b downstream end; 4 scroll casing; 4a peripheral wall; 4b tongue portion; 4c sidewall; 4e scroll portion; 5 suction opening; 6, 9 fan motor; 6a output shaft; 7, 16 case; 9a motor support; 10 heat exchanger; 16a upper surface portion; 16b lower surface portion; 16c side surface portion; 17, 72 case discharge opening; 18, 71 case suction opening; 19, 73 partition plate; 30 air-blowing apparatus; 31 curved portion; 40 air-conditioning apparatus; 41 discharge opening; 41a, 41b end portion; 42 step; 43 connecting portion; 44 engaging portion; 45 flat surface portion; 46 curved surface portion; 50 refrigeration cycle apparatus; 100 outdoor unit; 101 compressor; 102 four-way valve; 103 outdoor heat exchanger; 104 outdoor air blower; 105 throttle device; 200 indoor unit; 201 load heat exchanger; 202 load air blower; 300 gas pipe; 400 liquid pipe.
| Number | Date | Country | Kind |
|---|---|---|---|
| PCT/JP2017/038960 | Oct 2017 | JP | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2018/039585 | 10/25/2018 | WO | 00 |
