JP6856165B2 - Blower and refrigeration system with a blower - Google Patents

Description

The present invention relates to a blower and a refrigerating device having a blower.

Conventionally, a blower for generating an air flow is known in an air conditioner or the like. For example, Patent Document 1 (International Publication No. 2015/125486) discloses a blower that generates an air flow flowing in the direction of the rotation axis. Patent Document 1 includes a plurality of blades extending radially from the core portion when viewed from the direction of the rotation axis, a ring portion connected to the tip of each blade, and a cylindrical rectifying member extending along the direction of the rotation axis. doing.

In a blower as in Patent Document 1, a gap is formed between the ring portion and the rectifying member so that the ring portion can rotate together with the blade, and the secondary side (blowing) is formed through the gap. A part of the air flow on the side) flows backward toward the primary side (suction side). The backflow air (backflow air) in this embodiment merges with the air sucked into the fan (suction air) (ie, a short circuit can occur). In Patent Document 1, a brim for rectifying the flow of backflow air at the tip of the ring portion in order to suppress noise generated at the time of merging due to the backflow air forming a vortex before merging with the suction air. A portion is provided to prevent the formation of a vortex due to backflow air.

In the blower as described above, the air volume blown out from the fan becomes small in relation to the large flow rate (backflow) of the backflow air. In this respect, by reducing the reverse flow rate, the air volume is increased and the efficiency of the blower is improved. However, Patent Document 1 focuses on suppressing the generation of vortices and suppressing noise by rectifying the flow of backflow air, and special consideration is given to reducing the backflow rate (that is, improving the efficiency of the blower). Not.

Therefore, an object of the present invention is to improve the efficiency of the blower.

The blower according to the first aspect of the present invention includes a core portion, a plurality of blades, a ring portion, and a rectifying member. The core portion is connected to the drive source. The plurality of blades extend radially from the core portion when viewed from the direction of the rotation axis. The ring portion is connected to the tip of each blade on the radial outer side of each blade. The ring portion has a ring shape when viewed from the direction of the rotation axis. The rectifying member is arranged at a radial distance from the ring portion. The rectifying member is a cylindrical member extending along the direction of the rotation axis. The rectifying member rectifies the air sent by the blades. The ring portion has a first portion, a second portion, and a third portion. The first part includes the first end part. The first end portion is positioned so as to overlap the end portion of the rectifying member when viewed from the radial direction. The end of the rectifying member is the windward end of the rectifying member. The first part extends along the rotation axis direction inside the rectifying member in the radial direction. The second part includes the second end. The second end is located at a distance from the end of the rectifying member in the direction of the rotation axis. The second end portion overlaps with the rectifying member when viewed from the direction of the rotation axis. The second portion is connected to the first end and extends radially to the second end. The third part is connected to the second end. The third portion extends along the radial direction on the radial outer side of the end of the rectifying member. The second end is located so as to overlap the virtual point. The virtual point is located at a position where the end of the rectifying member is linearly extended to the windward side along the direction of the rotation axis. The first dimension is 0.5 times or more the first distance. The first dimension is the radial length of the third part. The first distance is a linear distance between the end of the rectifying member and the virtual point.

In the blower according to the first aspect of the present invention, the ring portion is connected to the second end portion that overlaps the virtual point located at a location where the end portion of the rectifying member is linearly extended to the wind side along the direction of the rotation axis. It has a third part that extends along the radial direction on the radial outside of the end of the rectifying member, and the first dimension (the radial length of the third part) is the first distance (the end of the rectifying member and a virtual point). It is 0.5 times or more of the linear distance with. That is, the third portion extends radially outward from the end portion of the rectifying member by a length corresponding to 0.5 times or more of the gap formed between the ring portion and the rectifying member. As a result, the third part becomes resistance of the backflow air (air flowing back through the gap between the ring part and the rectifying member) toward the confluence with the suction air (air sucked into the fan), and heads toward the confluence. It is possible to largely bypass the backflow air. In connection with this, the flow path resistance increases with respect to the backflow air toward the confluence, and the backflow rate (amount of backflow air) per unit time is reduced. Therefore, the efficiency of the blower is improved.

Regarding "extending along the rotation axis direction / radial direction" here, not only the case where the extension is strictly in the rotation axis direction / radial direction but also the case where the extension is inclined in the rotation axis direction / radial direction. included. The "diameter inner side" refers to the inner peripheral side of the blower, the "diameter outer side" refers to the outer peripheral side of the blower, and the "windward side" refers to the side closer to the suction side of the blower.

Further, the “ring shape” here includes not only the case where the ring shape is strictly formed but also the case where the ring shape is formed as a whole while meandering or bending. Further, the "cylindrical shape" has not only a case of strictly cylindrical shape, but also a flare shape in which the cross-sectional area on one end side gradually expands toward one end, and a constricted portion in which the cross-sectional area gradually narrows between both ends. It also includes the case of exhibiting a substantially cylindrical shape such as an hourglass shape.

The blower according to the second aspect of the present invention is the blower according to the first aspect, and the third part extends along a direction orthogonal to the direction in which the rectifying member extends. As a result, it is possible to make a simple structure and largely bypass the backflow air toward the confluence with the suction air. In this connection, it is possible to reduce the reverse flow rate while suppressing the cost.

The blower according to the third aspect of the present invention is the blower according to the first aspect or the second aspect, and the third part extends radially outward from the end of the rectifying member and then rotates. It extends along the axial direction. The end of the rectifying member is located radially inside the third portion. The end portion of the rectifying member overlaps with the third portion when viewed in the radial direction. This makes it possible to further detour the backflow air toward the confluence with the suction air. In this connection, the reverse flow rate will be further reduced and the efficiency of the blower will be further improved.

The blower according to the fourth aspect of the present invention is a blower according to any one of the first to third aspects, and the rectifying member is a bell mouth arranged on the leeward side of the blade. As a result, the backflow air passing through the gap between the bell mouth arranged on the blowout side of the wing and the ring portion can be largely diverted. Therefore, the efficiency of the blower having the bell mouth and the ring portion is improved.

The blower according to the fifth aspect of the present invention is a blower according to any one of the first to fourth aspects, and the first distance is 5 mm or more and -15 mm or less. The first dimension is 4 mm or more. As a result, it is possible to reliably bypass the backflow air toward the confluence with the suction air while suppressing the increase in size of the blower.

The blower according to the sixth aspect of the present invention is the blower according to any one of the first to fifth aspects, and is an axial fan that sends air in the direction of the rotation axis. This improves the efficiency of the axial fan having the rectifying member and the ring portion.

The refrigerating apparatus according to the seventh aspect of the present invention includes the blower and the heat exchanger according to any one of the first to sixth aspects. The heat exchanger includes a heat transfer tube through which the refrigerant flows. The heat exchanger exchanges heat between the air flow generated by the blower and the refrigerant.

In the refrigerating apparatus according to the seventh aspect of the present invention, the efficiency of the blower is improved, and the amount of heat exchange in the heat exchanger can be increased. Therefore, it is possible to improve the capacity of the refrigerating apparatus.

In the blower according to the first aspect of the present invention, the third part flows through the gap formed between the ring part and the rectifying member toward the confluence point with the suction air (air sucked into the fan). It becomes a resistance of the backflow air), and it becomes possible to largely bypass the backflow air toward the confluence. In connection with this, the flow path resistance increases with respect to the backflow air toward the confluence, and the backflow rate (amount of backflow air) per unit time is reduced. Therefore, the efficiency of the blower is improved.

In the blower according to the second aspect of the present invention, it is possible to reduce the reverse flow rate while suppressing the cost.

In the blower according to the third aspect of the present invention, the reverse flow rate is further reduced, and the efficiency of the blower is further improved.

In the blower according to the fourth aspect of the present invention, the efficiency of the blower having the bell mouth and the ring portion is improved.

In the blower according to the fifth aspect of the present invention, it is possible to reliably bypass the backflow air toward the confluence with the suction air while suppressing the increase in size of the blower.

In the blower according to the sixth aspect of the present invention, the efficiency of the axial fan having the rectifying member and the ring portion is improved.

In the refrigerating apparatus according to the seventh aspect of the present invention, the efficiency of the blower is improved, and the amount of heat exchange in the heat exchanger can be increased. Therefore, it is possible to improve the capacity of the refrigerating apparatus.

The schematic block diagram of the refrigerating apparatus which concerns on one Embodiment of this invention. External view of the refrigeration system. The schematic diagram which roughly showed the target space and the heat exchanger accommodation space on a heat source side. A perspective view of the heat source side fan as seen from the outlet side. Front view of the heat source side fan as seen from the outlet side. FIG. 5 is a sectional view taken along line VI-VI of FIG. A perspective view of the fan rotor as seen from the outlet side. Front view of the fan rotor as seen from the outlet side. Front view of the fan rotor as seen from the suction side. An enlarged view of the X portion of FIG. FIG. 10 is a schematic view showing a state in which the shroud is replaced with a shroud having no third stretched portion. The graph which showed an example of the pressure gain when the blower having a shroud of FIG. 10 and the blower having a shroud of FIG. 11 was driven under the same conditions. FIG. 10 is a schematic view showing a state in which the shroud is replaced with the shroud according to the modified example A. The graph which showed an example of the pressure gain when the blower having a shroud of FIG. 10, the blower having a shroud of FIG. 11 and the blower having a shroud of FIG. 13 was driven under the same conditions.

Hereinafter, the heat source side fan 30 (blower) and the refrigerating apparatus 100 according to the embodiment of the present invention will be described with reference to the drawings. The following embodiments are specific examples of the present invention, do not limit the technical scope of the present invention, and can be appropriately modified without departing from the gist of the invention.

(1) Refrigerator 100
FIG. 1 is a schematic configuration diagram of a refrigerating apparatus 100 according to an embodiment of the present invention. The refrigerating device 100 is a device that cools the target space S1 such as in a low temperature warehouse, in a shipping container, or in a store showcase. The refrigerating apparatus 100 includes a refrigerant circuit RC, and during operation, the refrigerant is compressed, cooled or condensed, depressurized, heated or evaporated, and then compressed again in the refrigerant circuit RC. Perform a cycle. The refrigerant enclosed in the refrigerant circuit RC is appropriately selected according to the design specifications and the installation environment.

In the refrigerating apparatus 100, the refrigerant circuit RC is configured by connecting various circuit elements via the refrigerant pipes. Specifically, the refrigerating apparatus 100 mainly includes a compressor 11, a heat source side heat exchanger 12, a receiver 13, a supercooling heat exchanger 14, a heat source side first expansion valve 15, and a heat source side second expansion valve as circuit elements. 16. It has a check valve 17, a heating pipe 21, a user-side expansion valve 22, and a user-side heat exchanger 23.

Further, the refrigerating apparatus 100 has a heat source side fan 30 and a utilization side fan 31 as a blower that generates an air flow that serves as a cooling source or a heating source for the refrigerant. Further, the refrigerating device 100 has a remote controller 35 as an input device for the user to input various commands. Further, the refrigerating device 100 has a controller 36 that controls the operation of each actuator according to the situation.

(1-1) Equipment included in the refrigerating apparatus 100 The compressor 11 is equipment for compressing the refrigerant. In the present embodiment, the compressor 11 has a closed structure in which a positive displacement compression element (not shown) such as a rotary type or a scroll type is rotationally driven by a compressor motor (not shown). Further, here, the compressor motor can control the operating frequency by an inverter, whereby the capacity of the compressor 11 can be controlled.

The heat source side heat exchanger 12 (corresponding to the “heat exchanger” described in the claims) is a heat exchanger that functions as a condenser (or radiator) for a high-pressure refrigerant in the refrigeration cycle. The heat source side heat exchanger 12 includes a plurality of heat transfer tubes 121 (see FIG. 4) and heat transfer fins. The heat source side heat exchanger 12 is configured to exchange heat between the refrigerant in the heat transfer tube 121 and the outside air passing around the heat transfer tube 121 (outside air flow F1 described later). ing.

The receiver 13 is a container for temporarily storing the condensed refrigerant in the heat source side heat exchanger 12.

The supercooling heat exchanger 14 is a heat exchanger that cools the refrigerant temporarily stored in the receiver 13, and is arranged on the downstream side of the refrigerant flow of the receiver 13. In the supercooling heat exchanger 14, the first flow path 141 and the second flow path 142 are individually configured, and the refrigerant flowing through the first flow path 141 and the second flow path 142 is configured to perform heat exchange. Has been done.

The first expansion valve 15 on the heat source side is an electric expansion valve capable of controlling the opening degree, and is arranged on the downstream side of the refrigerant flow of the supercooling heat exchanger 14. The heat source side first expansion valve 15 depressurizes the refrigerant that has passed through the first flow path 141 according to its opening degree.

The heat source side second expansion valve 16 is an electric expansion valve whose opening degree can be controlled, and is arranged on the upstream side of the refrigerant flow in the second flow path 142 of the supercooling heat exchanger 14. ing. The heat source side second expansion valve 16 reduces the pressure of the refrigerant flowing into the second flow path 142 according to the opening degree thereof.

The check valve 17 is arranged on the refrigerant flow downstream side of the heat source side heat exchanger 12 and on the refrigerant flow upstream side of the receiver 13. The check valve 17 allows the flow of the refrigerant from the heat source side heat exchanger 12 side and shuts off the flow of the refrigerant from the receiver 13 side.

The heating pipe 21 is a refrigerant pipe through which a high-pressure refrigerant flows, and is a pipe for melting frost and ice blocks adhering to a drain pan (not shown) that receives drain water generated in the user-side heat exchanger 23.

The utilization-side expansion valve 22 functions as a depressurizing means (expansion means) for the high-pressure refrigerant. The utilization side expansion valve 22 is arranged on the upstream side of the refrigerant flow of the utilization side heat exchanger 23. The utilization side expansion valve 22 depressurizes the inflowing refrigerant according to the opening degree.

The user-side heat exchanger 23 is a heat exchanger that functions as a refrigerant evaporator. The user-side heat exchanger 23 is arranged in the target space S1 (inside the refrigerator), and is a heat exchanger for cooling the air in the refrigerator in the target space S1. The user-side heat exchanger 23 includes a plurality of heat transfer tubes and heat transfer fins (not shown). The user-side heat exchanger 23 is configured to exchange heat between the refrigerant in the heat transfer tube and the air passing around the heat transfer tube.

The heat source side fan 30 is a blower for sucking air (outside air) outside the target space S1 to exchange heat with the refrigerant flowing through the heat source side heat exchanger 12 and then discharging the air to the outside. The heat source side fan 30 supplies the heat source side heat exchanger 12 with outside air as a cooling source for the refrigerant flowing through the heat source side heat exchanger 12. The heat source side fan 30 includes a heat source side fan motor M30 which is a drive source, and receives an outside air flow F1 which passes through the heat source side heat exchanger 12 outside the target space S1 (outside the refrigerator) when the heat source side fan motor M30 is driven. Generate (see the two-dot chain arrow in FIG. 3). The details of the heat source side fan 30 will be described later.

The user-side fan 31 is a blower for sucking in the air (internal air) in the target space S1, passing it through the user-side heat exchanger 23 to exchange heat with the refrigerant, and then sending it back to the target space S1. The user-side fan 31 is arranged in the target space S1, and the user-side fan 31 supplies the internal air as a heating source of the refrigerant flowing through the user-side heat exchanger 23 to the user-side heat exchanger 23. The user-side fan 31 includes a user-side fan motor (not shown) that is a drive source, and has an internal air flow F2 (FIG. 3) that passes through the user-side heat exchanger 23 in the target space S1 when the user-side fan motor is driven. (See dashed arrow).

The remote controller 35 has an input key for the user to input various commands. The remote controller 35 is configured to be able to communicate with the controller 36, and transmits a signal corresponding to the input command to the controller 36.

The controller 36 includes a microcomputer including a CPU, a memory, and the like. The controller 36 is electrically connected to each actuator (11, 15, 16, 30, 31, etc.) included in the refrigerating device 100 and various sensors, and inputs and outputs signals to and from each other. The controller 36 controls the operation of each actuator according to the situation.

(1-2) Flow of Refrigerant in Refrigerant Device 100 In the refrigerating device 100, the refrigerant filled in the refrigerant circuit RC during operation is mainly the compressor 11, the heat source side heat exchanger 12, the receiver 13, and the overcooling heat exchange. A cooling operation is performed in which the vessel 14, the first expansion valve 15 on the heat source side, the expansion valve 22 on the utilization side, and the heat exchanger 23 on the utilization side circulate in this order. In this cooling operation, a part of the refrigerant that has passed through the first flow path 141 of the supercooling heat exchanger 14 is branched, and the second expansion valve 16 on the heat source side and the supercooling heat exchanger 14 (second flow path 142) are branched. ), It is returned to the compressor 11.

When the cooling operation is started, the refrigerant is sucked into the compressor 11 and compressed in the refrigerant circuit RC, and then discharged. In the compressor 11, capacity control is performed according to the required cooling load. Specifically, the operating frequency of the compressor 11 is controlled so that the suction pressure becomes a target value set according to the cooling load. The gas refrigerant discharged from the compressor 11 flows into the heat source side heat exchanger 12.

The gas refrigerant that has flowed into the gas side of the heat source side heat exchanger 12 exchanges heat with the outside air sent by the heat source side fan 30 in the heat source side heat exchanger 12, dissipates heat and condenses, and heat exchange on the heat source side. It flows out of the vessel 12.

The refrigerant flowing out of the heat source side heat exchanger 12 flows into the receiver 13. The refrigerant that has flowed into the receiver 13 is temporarily stored as a saturated liquid refrigerant in the receiver 13, and then flows out from the receiver 13.

The liquid refrigerant flowing out of the receiver 13 flows into the first flow path 141 of the supercooling heat exchanger 14. The liquid refrigerant flowing into the first flow path 141 exchanges heat with the refrigerant flowing through the second flow path 142 in the supercooling heat exchanger 14 and is further cooled to become a supercooled liquid refrigerant, and becomes the first flow. It flows out from the road 141.

A part of the liquid refrigerant flowing out from the first flow path 141 of the supercooling heat exchanger 14 branches and flows into the second expansion valve 16 on the heat source side. The refrigerant that has flowed into the second expansion valve 16 on the heat source side is reduced to an intermediate pressure and then flows into the second flow path 142 of the supercooling heat exchanger 14. The refrigerant flowing into the second flow path 142 exchanges heat with the refrigerant flowing through the first flow path 141. The refrigerant flowing out of the second flow path 142 is returned (injected) in the middle of the compression stroke of the compressor 11.

On the other hand, the other part of the liquid refrigerant flowing out from the first flow path 141 of the supercooled heat exchanger 14 flows into the first expansion valve 15 on the heat source side. The liquid refrigerant that has flowed into the first expansion valve 15 on the heat source side passes through the heating pipe 21 and flows into the expansion valve 22 on the utilization side after the decompression / flow rate is adjusted according to the opening degree of the first expansion valve 15 on the heat source side. .. The refrigerant that has flowed into the user-side expansion valve 22 is decompressed according to the opening degree of the user-side expansion valve 22, and flows into the user-side heat exchanger 23.

The refrigerant that has flowed into the user-side heat exchanger 23 exchanges heat with the internal air sent by the user-side fan 31 and evaporates to become a gas refrigerant, which flows out of the user-side heat exchanger 23. The gas refrigerant flowing out of the user-side heat exchanger 23 is sucked into the compressor 11 again.

(1-3) Configuration of Refrigerating Device 100 FIG. 2 is an external view of the refrigerating device 100. The refrigerating device 100 has a casing 40 that constitutes a substantially rectangular parallelepiped outer shell. A remote controller 35 is arranged on the front surface of the casing 40, and a suction port H1 for flowing in the outside air flow F1 and an outlet H2 for letting out the outside air flow F1 are formed. The heat source side fan 30 is exposed from the outlet H2. The casing 40 is formed with an entrance / exit for entering / exiting the target space S1, and a door is openably / closably attached to the entrance / exit (not shown).

A target space S1 and a heat source side heat exchanger accommodating space S2 are formed in the casing 40. FIG. 3 is a schematic view schematically showing the target space S1 and the heat source side heat exchanger accommodating space S2. The target space S1 and the heat source side heat exchanger accommodating space S2 are partitioned by a partition plate 41.

The target space S1 is a space for accommodating and cooling the object to be cooled, and is shielded from the space outside the refrigerator. Various devices such as a heating pipe 21, a user-side expansion valve 22, a user-side heat exchanger 23, and a user-side fan 31 are arranged in the target space S1. In the target space S1, the user-side fan 31 is driven during operation to generate an air flow F2 in the refrigerator as shown by the broken line arrow in FIG. The internal air flow F2 is a flow of internal air that is sucked into the user-side fan 31 in the target space S1, passes through the user-side heat exchanger 23, and is then blown out to the target space S1.

In the heat source side heat exchanger accommodation space S2, a compressor 11, a heat source side heat exchanger 12, a receiver 13, a supercooling heat exchanger 14, a heat source side first expansion valve 15, a heat source side second expansion valve 16, and a heat source side Various devices such as a fan 30 are arranged. In the heat source side heat exchanger accommodating space S2, the heat source side fan 30 is driven during operation to generate an outside air flow F1 as shown by the two-point chain line arrow in FIG. The air flow F1 outside the refrigerator flows into the heat source side heat exchanger accommodating space S2 from outside the casing 40 through the suction port H1, is sucked into the heat source side fan 30, passes through the heat source side heat exchanger 12, and then blows out. This is a flow of air flowing out of the casing 40 via H2.

(2) Details of Heat Source Side Fan 30 (2-1) Configuration of Heat Source Side Fan 30 FIG. 4 is a perspective view of the heat source side fan 30 as seen from the outlet side. FIG. 5 is a front view of the heat source side fan 30 as seen from the blowout side. FIG. 6 is a sectional view taken along line VI-VI of FIG. The arrow "F1" in FIGS. 4 and 6 indicates the flow direction of the outside air flow F1.

In the following description, the direction in which the rotation axis A1 of the heat source side fan 30 extends is referred to as the rotation axis direction dr1 (see FIG. 6). Further, the radial direction of the heat source side fan 30 is referred to as a radial direction dr2 (see FIG. 6). Further, the expression "extending along the rotation axis direction dr1 / radial direction dr2" is defined not only in the case of strictly extending toward the rotation axis direction dr1 / radial direction dr2 but also in the rotation axis direction dr1 / radial direction dr2. It also includes the case where it is inclined and extended at a rate of (for example, within 45 degrees). Further, "inside of the radial dr2" refers to the inner peripheral side of the heat source side fan 30, and "outside of the radial dr2" refers to the outer peripheral side of the heat source side fan 30. Further, "leeward side" refers to the side closer to the suction side of the heat source side fan 30, and "leeward side" refers to the side closer to the blow side of the heat source side fan 30.

As shown in FIGS. 4 and 6, the heat source side fan 30 is connected to the heat source side heat exchanger 12 having four heat exchange surfaces and having a substantially rectangular cross section via a fixing member (not shown). There is. More specifically, the heat source side fan 30 has a suction side on the leeward side of the outside air flow F1 with respect to the heat source side heat exchanger 12 arranged so as to have a substantially rectangular shape when viewed from the rotation axis direction dr1. They are connected so that they are located.

The heat source side fan 30 is an axial fan that sends air in the axial flow direction (rotational axial direction dr1), and is a so-called propeller fan. The heat source side fan 30 mainly has a fan rotor 50, a bell mouth 65, and a front plate 70.

FIG. 7 is a perspective view of the fan rotor 50 as seen from the blowing side. FIG. 8 is a front view of the fan rotor 50 as seen from the outlet side. FIG. 9 is a front view of the fan rotor 50 as seen from the suction side.

In the present embodiment, the dimensions of the rotation axis direction dr1 and the radial direction dr2 of the fan rotor 50 are appropriately set according to the dimensions of the heat source side heat exchanger 12. The fan rotor 50 includes a core portion 51, a plurality of (here, 10 blades) blades 55, and a shroud 60 (ring portion).

The core portion 51 has an annular shape when viewed from the rotation axis direction dr1. The core portion 51 includes a bearing portion 52, and is mechanically connected to the output shaft of the heat source side fan motor M30 in the bearing portion 52. The central portion of the core portion 51 is superimposed on the rotation axis A1. The core portion 51 includes a substantially cylindrical side surface portion 53 extending along the rotation axis direction dr1. The side surface portion 53 is made of synthetic resin.

The plurality of blades 55 (corresponding to the "wings" described in the claims) extend radially from the core portion 51 when viewed from the rotation axis direction dr1 (note that, in each figure, some of the blades 55 The reference code is omitted). Each blade 55 extends from the core portion 51 along the radial direction dr2 while being curved. More specifically, each blade 55 is curved so as to bulge counterclockwise when viewed from the outlet side. The blade 55 is made of synthetic resin, and one end thereof is welded to the side surface portion 53 of the core portion 51. The other end (tip) of the blade 55 is welded to the shroud 60.

In the shroud 60 (corresponding to the “ring portion” described in the claims), the outside air (secondary side air Fb; see FIG. 10) sent by the blade 55 has a flow F1 outside the chamber rather than the blade 55. It is a member for suppressing backflow from the leeward side (secondary side) to the leeward side (primary side). The shroud 60 is a member made of synthetic resin that has a ring shape when viewed from the rotation axis direction dr1. The shroud 60 is arranged on the outer side (that is, the outer peripheral side) of the radial dr2 of each blade 55, and is connected to the tip of each blade 55. In other words, the shroud 60 can be said to be a member that covers each blade 55 from the outer peripheral side.

The bell mouth 65 (corresponding to the "rectifying member" described in the claims) is arranged on the leeward side of the blade 55, and the secondary air Fb sent from the blade 55 is in the rotation axis direction dr1 (axial flow direction). It is a member for rectifying so as to be blown out along. The bell mouth 65 has a substantially cylindrical shape (more specifically, a flare shape in which the cross-sectional area on one end side gradually expands) extending along the rotation axis direction dr1. The fan rotor 50 is exposed to the leeward side from the opening portion of the bell mouth 65. The bell mouths 65 are spaced apart from the shroud 60 in the radial direction dr2. More specifically, a portion of the bell mouth 65 is located inside the radial dr2 of the shroud 60, and another portion of the bell mouth 65 is located outside the radial dr2 of the shroud 60. In the following description, the windward end of the bell mouth 65 will be referred to as the bell mouth windward end 66. The bellmouth windward end 66 corresponds to the "rectifying member end" described in the claims.

The front plate 70 is a plate-shaped member that constitutes one surface portion of the heat source side fan 30 on the blowout side of the outer shell. In the present embodiment, the front plate 70 is integrally molded with the bell mouth 65, and is continuously connected to the end portion on the leeward side of the bell mouth 65 (the blowing side of the air flow F1 outside the refrigerator). The front plate 70 has a substantially rectangular shape when viewed from the rotation axis direction dr1. An annular opening 70a for exposing the fan rotor 50 and blowing out the air flow F1 outside the refrigerator is formed in the central portion of the front plate 70. The dimensions of the front plate 70 are appropriately set according to the dimensions of the heat source side heat exchanger 12, and the size of the opening 70a is appropriately set according to the dimensions of the fan rotor 50 and the bell mouth 65.

(2-2) Details of the shroud 60 and the positional relationship between the shroud 60 and the bell mouth 65 FIG. 10 is an enlarged view of the X portion of FIG. As shown in FIG. 10, the shroud 60 has a substantially L-shaped cross section. More specifically, the shroud 60 is directed from one end that overlaps the bell mouth 65 and the radial dr2 inside (that is, the inner peripheral side) of the bell mouth 65 in the radial direction dr2 toward the wind side along the rotation axis direction dr1. After extending, it is curved toward the outside of the radial dr2, and is formed so as to extend along the radial dr2 to the other end located outside the radial dr2 of the bell mouth 65.

A gap C1 is formed between the shroud 60 and the bell mouth 65 so that the shroud 60 can rotate together with the blade 55. That is, the shroud 60 is not in contact with the bell mouth 65, and is partially displaced from the bell mouth 65 in the rotation axis direction dr1 and / or in the radial direction dr2.

The shroud 60 mainly has a first stretched portion 61 extending mainly along the rotation axis direction dr1, and a second stretched portion 62 and a third stretched portion 63 extending mainly along the radial direction dr2. The first stretched portion 61, the second stretched portion 62, and the third stretched portion 63 are continuously connected and integrally formed. There is no clear boundary between the first stretched portion 61 and the second stretched portion 62, or between the second stretched portion 62 and the third stretched portion 63, but for convenience of explanation, the first stretched portion 61 and the second stretched portion 61 are stretched. The portion 62 and the third stretched portion 63 will be described as independent portions.

The first stretched portion 61 (corresponding to the “first portion” described in the claims) is one end (that is, the leeward side of the shroud 60) that overlaps the bell mouth 65 and the radial dr2 inside the radial dr2 of the bell mouth 65. It is a portion extending from the end portion) toward the windward side along the rotation axis direction dr1. The first stretched end 611 (corresponding to the "first end" described in the claims), which is the windward end of the first stretched portion 61, is the bellmouth windward end 66 when viewed from the radial direction dr2. It is superimposed on (the windward end of the bell mouth 65).

The second stretched portion 62 (corresponding to the “second part” described in the claims) is connected to the first stretched end portion 611, extends toward the wind side along the rotation axis direction dr1, and then extends in the radial direction dr2. It is a portion that extends outward in the radial direction dr2 along the radial direction dr2 after being curved toward the outside of the. The second stretched end 621 (corresponding to the "second end" described in the claims), which is the outer end of the second stretched portion 62 in the radial direction dr2, is the bellmouth windward upper end 66 and the rotation axis. It is located at intervals in the direction dr1 and overlaps with the bell mouth 65 when viewed from the rotation axis direction dr1. More specifically, the second stretched end 621 superimposes on a virtual point P1 virtually arranged at a location where the bellmouth windward end 66 is linearly extended windward along the rotation axis direction dr1. ing.

The third stretched portion 63 (corresponding to the “third portion” described in the claims) is connected to the second stretched end portion 621 and is connected to the shroud 60 and the like toward the outside of the radial direction dr2 along the radial direction dr2. It is a part that extends to the end (the end on the windward side). The third stretched portion 63 extends outward in the radial direction dr2 from the bellmouth windward end portion 66 toward the outside in the radial direction dr2. In other words, the bellmouth wind upper end 66 is located inside the radial direction dr2 of the third extension 63, and the third extension 63 is in the direction orthogonal to the direction in which the bellmouth 65 extends (rotational axis direction dr1). It extends along (here, the radial direction dr2).

The dimension L1 (first dimension), which is the length of the third stretched portion 63 in the radial direction dr2, is a linear distance between the bellmouth wind upper end portion 66 and the virtual point P1 (that is, the bellmouth wind upper end portion 66 and the first dimension). 2 The distance from the stretched end 621) is 0.5 times or more the distance D1. Here, the distance D1 is set according to the dimensions of the fan rotor 50 and the bell mouth 65. In the present embodiment, the distance D1 is 5 mm or more and -15 mm or less, and the dimension L1 is 4 mm or more. Specifically, the distance D1 is 7 mm and the dimension L1 is 5 mm. Further, here, the linear distance D2 between one end of the shroud 60 (the end on the leeward side) and the bell mouth 65 in the radial direction dr2 is 6 mm.

(3) Improving the efficiency of the heat source side fan 30 and improving the capacity of the refrigerating device 100 In a blower such as the heat source side fan 30, the air (here, the secondary side air Fb) sent by the blades (here, the blade 55) is used. A ring portion (here, shroud 60) is provided as a member for suppressing backflow from the leeward side (secondary side) of the wing to the leeward side (primary side), but the ring portion rotates together with the wing. , The rectifying member (here, Bellmouth 65) needs to be arranged so as not to overlap with the rotation trajectory of the ring portion, and a gap (here, gap C1) needs to be formed between the ring portion and the rectifying member. is there. Since the gap communicates with the primary side and the air on the secondary side has a higher pressure than the primary side, a part of the air on the secondary side passes through the gap without passing through the rectifying member. It will flow back to the primary side. That is, even when the ring portion is provided to suppress the backflow, a part of the air on the secondary side flows back to the primary side.

The air that has flowed back to the primary side (backflow air) merges with the air that is sucked into the fan rotor 50 (suction air) (that is, short circuit), but the larger the flow rate (backflow) of the backflow air, the larger the flow rate (backflow) of the backflow air. , The amount of air blown from the blower becomes smaller, and the efficiency of the blower decreases.

FIG. 11 is a schematic view showing a state in which the shroud 60 is replaced with a shroud 60 ′ having no third stretched portion 63 in FIG. Unlike the shroud 60, the shroud 60'does not have the third stretched portion 63, so that the shroud 60'has a substantially J-shaped cross section.

As described above, when the heat source side fan 30 is driven, the outside air flow F1 is generated, and as shown in FIGS. 10 and 11, the primary side air (suction air) Fa is used as the secondary side air Fb by the blade 55. It is sent to the next side, and the secondary side air Fb is rectified by the bell mouth 65 and blown out from the opening 70a as blown air Fb1. A part of the secondary side air Fb is not blown out from the opening 70a, but escapes as backflow air Fb2 in the radial direction dr2 (more specifically, the centrifugal direction) through the gap C1 and then joins the primary side air Fa. The two-dot chain arrow shown as the air flow in FIGS. 10 and 11 is schematically shown for convenience of explanation. In reality, the backflow air is mainly discharged in the centrifugal direction. It will merge with the suction air.

As shown in FIG. 11, when the third extending portion 63 is not provided, the length of the portion extending outward of the radial dr2 of the shroud 60'is the linear distance between the bellmouth wind upper end portion 66 and the virtual point P1. The flow path resistance is small when the backflow air Fb2, which is less than 0.5 times the distance D1 and flows back to the outside of the radial direction dr2 through the gap C1, heads for the confluence point with the primary side air Fa. In relation to this, in the shroud 60', the secondary side air Fb tends to flow backward and the reverse flow rate is large as compared with the case where the shroud 60 has the third stretched portion 63.

On the other hand, in the heat source side fan 30, the shroud 60 is provided with a third stretched portion 63 extending from the second stretched end portion 621 along the radial direction dr2 toward the outside of the radial direction dr2 to the other end of the shroud 60. The dimension L1 (the length of the radial dr2 of the third stretched portion 63) is 0.5 times or more the distance D1 (the linear distance between the bellmouth wind upper end portion 66 and the virtual point P1). .. That is, the third stretched portion 63 largely covers the bellmouth windward end 66 on the windward side.

In the shroud 60 provided with such a third extending portion 63, when the backflow air Fb2 that has flowed back to the outside of the radial direction dr2 through the gap C1 heads toward the confluence point with the primary side air Fa, the backflow air Fb2 (That is, the outlet of the backflow air Fb2 and the confluence point of the primary side air Fa are greatly separated from each other) and the flow path resistance is increased. In relation to this, in the shroud 60, the secondary side air Fb is less likely to flow back as compared with the case where the shroud 60'does not have the third stretched portion 63, and the backflow rate is suppressed. Then, in the heat source side fan 30 having such a shroud 60, the amount of work is improved and the efficiency of the blower is improved in relation to the suppression of the reverse flow rate.

FIG. 12 is a graph showing an example of pressure gain when the blower having the shroud 60 of FIG. 10 and the blower having the shroud 60'of FIG. 11 are driven under the same conditions. 12A and 12B are based on the analysis results, and the pressure gain of the blower having the shroud 60'of the aspect shown in FIG. 11 is shown in (A), and the shroud 60 of the aspect shown in FIG. 10 is shown in (B). The pressure gain of the blower with is shown.

In FIG. 12, it is shown that the pressure gain of the blower with the shroud 60'is 96.32 (Pa) and the pressure gain of the blower with the shroud 60 is 102.38 (Pa). That is, it is shown that the pressure gain of the blower having the shroud 60 is larger than that of the blower having the shroud 60', the work amount is increased, and the air volume per unit time is increased. In the refrigerating apparatus 100 having the heat source side fan 30 including the shroud 60, the capacity of the refrigerating apparatus 100 can be improved because the amount of heat exchange in the heat source side heat exchanger 12 is improved.

(4) Features (4-1)
In the above embodiment, in the heat source side fan 30, the shroud 60 has a third stretched portion 63. The third stretched portion 63 is connected to a second stretched end portion 621 that superimposes on a virtual point P1 located at a location where the bellmouth windward end portion 66 is linearly extended windward along the rotation axis direction dr1. It extends along the radial direction dr2 outside the radial direction dr2 from the bellmouth windward end 66. Further, the dimension L1 (the length of the radial direction dr2 of the third stretched portion 63) is 0.5 times or more the distance D1 (the linear distance between the bellmouth windward end 66 and the virtual point P1). That is, the length of the third stretched portion 63 corresponding to 0.5 times or more of the gap formed between the shroud 60 and the bell mouth 65 is outside the diameter direction dr2 of the bell mouth windward end 66. Extends to.

As a result, the third stretched portion 63 flows backflow through the gap C1 formed between the backflow air Fb2 (shroud 60 and the bell mouth 65) toward the confluence with the suction air (primary side air Fa sucked into the fan). The air flowing through the air) is largely detoured, and a large flow path resistance is secured with respect to the backflow air Fb2 toward the confluence. In connection with this, the backflow rate per unit time (flow rate of backflow air Fb2) is to be reduced. Therefore, the efficiency of the heat source side fan 30 is improved.

(4-2)
In the above embodiment, in the heat source side fan 30, the third extending portion 63 extends along a direction orthogonal to the extending direction of the bell mouth 65. This makes it possible to largely bypass the backflow air Fb2 toward the confluence with the suction air with a simple configuration. In connection with this, it is possible to reduce the reverse flow rate while suppressing the cost.

(4-3)
In the above embodiment, in the heat source side fan 30, the rectifying member is a bell mouth 65 arranged on the leeward side of the blade 55. As a result, it is possible to largely bypass the backflow air Fb2 passing through the gap C1 between the bell mouth 65 and the shroud 60 arranged on the blowout side of the blade 55. Therefore, the efficiency of the heat source side fan 30 having the bell mouth 65 and the shroud 60 is improved.

(4-4)
In the above embodiment, in the heat source side fan 30, the distance D1 is 7 mm (that is, 5 mm or more and -15 mm or less), and the dimension L1 is 5 mm (that is, 4 mm or more). As a result, it is possible to reliably bypass the backflow air Fb2 toward the confluence with the suction air while suppressing the increase in size of the heat source side fan 30.

(4-5)
In the above embodiment, the heat source side fan 30 is an axial fan that sends air in the direction of the rotation axis direction dr1, and the efficiency of the axial fan having the shroud 60 (ring portion) and the bell mouth 65 (rectifying member) is improved. ing.

(4-6)
In the above embodiment, the efficiency of the heat source side fan 30 is improved, and it is possible to increase the amount of heat exchange in the heat source side heat exchanger 12. Therefore, the capacity of the refrigerating device 100 can be improved.

(5) Modification Example The above embodiment can be appropriately modified as shown in the following modification examples. In addition, each modification may be applied in combination with another modification as long as there is no contradiction.

(5-1) Modification A
In the above embodiment, the heat source side fan 30 has the shroud 60 of the aspect shown in FIG. 10, but is configured to have a shroud 60a having a U-shaped cross section as shown in FIG. 13 instead of the shroud 60. May be done.

The shroud 60a has a third stretched portion 63a instead of the third stretched portion 63, and also has a fourth stretched portion 64 extending leeward along the rotation axis direction dr1.

The third extending portion 63a extends along the radial direction dr2 outside the radial direction dr2 from the bellmouth windward end portion 66, and then extends along the rotation axis direction dr1. More specifically, the third stretched portion 63a extends outward in the radial direction dr2 from the connecting portion with the second stretched end portion 621 while curving toward the leeward side along the rotation axis direction dr1. ing. The third stretched end 631 which is the leeward end of the third stretched portion 63a is located on the leeward side of the bellmouth windward end 66, and the third stretched portion 63a is a bell when viewed from the radial direction dr2. It overlaps with the mouse windward end 66.

The fourth stretched portion 64 extends from the third stretched end portion 631 toward the leeward side along the rotation axis direction dr1 on the outside of the radial direction dr2 of the bell mouth 65. The fourth stretched portion 64 includes a fourth stretched end portion 641 that overlaps with the first stretched portion 61 (more specifically, the leeward end portion of the shroud 60a) when viewed from the radial direction dr2. That is, the fourth stretched portion 64 is arranged together with the first stretched portion 61 so as to partially sandwich the bell mouth 65. The fourth stretched end 641 corresponds to the other end of the shroud 60a (the end opposite to the leeward end).

Even with such a shroud 60a, the dimension L1', which is the length of the third stretched portion 63a in the radial direction dr2, is the distance D1 which is the linear distance between the bellmouth windward end 66 and the virtual point P1. It is 0.5 times or more. That is, the third stretched portion 63a largely covers the bellmouth windward end 66 on the windward side.

Even when the third stretched portion 63a is provided in such an embodiment, the backflow air Fb2 that has flowed back to the outside of the radial direction dr2 through the gap C1 is different from the primary side air Fa as compared with the shroud 60'in FIG. When heading to the confluence, the backflow air Fb2 largely detours and the flow path resistance increases.

In particular, the shroud 60a has a fourth stretched portion 64 that is connected to the third stretched end portion 631 and extends leeward along the rotation axis direction dr1 outside the radial direction dr2 of the bell mouth 65. That is, the fourth stretched portion 64 covers the bellmouth windward end portion 66 on the outside of the radial direction dr2. As a result, the area of the portion that becomes the resistance of the backflow air Fb2 is secured even larger than that of the shroud 60, so that the backflow air Fb2 detours even more (that is, the outlet of the backflow air Fb2 and the primary side air Fa). The distance from the confluence point is further increased), and the flow path resistance is further increased. In this connection, in the shroud 60a, the secondary side air Fb is less likely to flow backward, and the reverse flow rate is further suppressed.

When the shroud 60a is provided, the work load of the heat source side fan 30 is further improved as compared with the case where the shroud 60 is provided, and the efficiency of the blower is improved in relation to the fact that the reverse flow rate is particularly suppressed. improves.

FIG. 14 shows an example of the pressure gain when the blower having the shroud 60 of FIG. 10, the blower having the shroud 60'of FIG. 11 and the blower having the shroud 60a of FIG. 13 are driven under the same conditions. It is a graph. FIG. 14 is based on the analysis result, and shows the pressure gain of the blower having the shroud 60'of the aspect shown in FIG. 11 in (A), and the shroud 60 of the aspect shown in FIG. 10 in (B). The pressure gain of the blower having the blower is shown, and in (C), the pressure gain of the blower having the shroud 60a of the aspect shown in FIG. 13 is shown.

In FIG. 14, the pressure gain of the blower having the shroud 60'is 96.32 (Pa), the pressure gain of the blower having the shroud 60 is 102.38 (Pa), and the pressure gain of the blower having the shroud 60a. Is shown to be 104.94 (Pa). That is, it is shown that the blower having the shroud 60a has a larger pressure gain than the blower having the shroud 60'or the shroud 60, the work load is increased, and the air volume per unit time is increased.

(5-2) Modification B
In the above embodiment, the third extending portion 63 extends along a direction orthogonal to the extending direction of the bell mouth 65. However, the third extending portion 63 is directed with respect to the direction in which the bell mouth 65 extends on the wind side of the bell mouth wind upper end portion 66 so that the outlet of the backflow air Fb2 and the confluence point of the primary side air Fa are greatly separated from each other. As long as it extends along the intersecting direction, it does not necessarily have to extend along the direction orthogonal to the direction in which the bell mouth 65 extends.

(5-3) Modification C
In the above embodiment, in the shroud 60, the case where the first stretched portion 61, the second stretched portion 62, and the third stretched portion 63 are continuously connected (that is, the case where they are integrally molded) has been described. However, the shroud 60 does not necessarily have to be configured in such an embodiment, and any / all of the first stretched portion 61, the second stretched portion 62, and the third stretched portion 63, which are separately configured, are appropriately joined. It may be configured by.

(5-4) Modification D
In the above embodiment, in order to suppress the backflow of the backflow air Fb2 through the gap C1 between the rectifying member (bell mouth 65 arranged on the leeward side of the blade 55) and the ring portion (shroud 60), a third The case where the extending portion 63 is arranged on the windward side of the windward end portion (bellmouth windward end portion 66) of the rectifying member has been described.

However, the technical idea of the present invention can be appropriately applied to other environments as well. For example, when the blower has a rectifying member arranged on the windward side of the blade 55, the ring portion has a third extension portion in order to suppress the backflow of backflow air through the gap between the rectifying member and the ring portion. A stretched portion corresponding to 63 (specifically, a stretched portion that largely covers the windward side of the windward end of the rectifying member in the same manner as the third stretched portion 63 of the above embodiment) may be provided. ..

(5-5) Modification E
In the above embodiment, the case where the distance D1 is 7 mm and the dimension L1 is 5 mm has been described. However, the value of the distance D1 or the dimension L1 is not necessarily limited to such a value, and can be appropriately changed according to the design specifications and the installation environment. For example, the distance D1 may be 6 mm (ie, less than 7 mm) or 8 mm (ie, 8 mm or more). Further, for example, the dimension L1 may be 4 mm (that is, less than 5 mm) or 6 mm (that is, 6 mm or more).

Further, in the above embodiment, the case where the distance D1 is 5 mm or more and -15 mm or less and the dimension L1 is 4 mm or more has been described. However, the value of the distance D1 or the dimension L1 does not necessarily have to be set based on the numerical range, and may be set based on a different numerical range according to the design specifications and the installation environment. However, from the viewpoint of suppressing the reverse flow rate, the gap between the ring portion and the rectifying member is preferably small, and the distance D1 is preferably 15 mm or less. On the other hand, the distance D1 is preferably 5 mm or more so that the ring portion can be smoothly rotated.

(5-6) Modification F
In the above embodiment, the heat source side fan 30 is connected to the heat source side heat exchanger 12 having four heat exchange surfaces and having a substantially rectangular cross section. However, the heat source side fan 30 does not necessarily have to be connected to a heat exchanger having a substantially rectangular cross section having four heat exchange surfaces, and a heat exchanger of another shape (for example, three or less or five surfaces). It may be connected to a heat exchanger having the above heat exchange surface and having a substantially L-shaped, U-shaped or polygonal cross section). Further, the heat source side fan 30 does not necessarily have to be connected to the heat exchanger, and may be installed independently.

(5-7) Modification G
In the above embodiment, the core portion 51 (side surface portion 53), the blade 55, and the shroud 60 are made of synthetic resin. However, the core portion 51, the blade 55 and / or the shroud 60 do not necessarily have to be made of synthetic resin, and may be made of another material (for example, metal).

Further, in the above embodiment, the case where the fan rotor 50 is formed by welding the core portion 51, the blade 55, and the shroud 60 has been described. However, the configuration of the fan rotor 50 is not necessarily limited to this, and the core portion 51 and the blade 55, and / or the blade 55 and the shroud 60 may be connected by another method (for example, brazing). Further, any / all of the core portion 51, the blade 55, and the shroud 60 may be integrally molded. In such a case, in the manufacturing process of the fan rotor 50, the step of connecting the core portion 51 and the blade 55 and / or the blade 55 and the shroud 60 is omitted.

(5-8) Modification H
In the above embodiment, the bell mouth 65 is integrally molded with the front plate 70, and the leeward end of the bell mouth 65 and the front plate 70 are continuously connected. However, the bell mouth 65 does not necessarily have to be integrally molded with the front plate 70, and may be configured separately. In such a case, the bell mouth 65 may be appropriately joined to the front plate 70.

(5-9) Modification I
In the above embodiment, the fan rotor 50 has 10 blades 55. However, the number of blades 55 can be appropriately changed according to the design specifications and the installation environment. For example, the number of blades 55 may be 4 (less than 10) or 12 (11 or more). Good.

(5-10) Modification J
In the above embodiment, the shroud 60 is configured to have a ring shape. However, the shroud 60 does not necessarily have to be formed in a ring shape as long as it is rotatably configured together with the blade 55, and may be configured to exhibit another shape. For example, the shroud 60 may be configured to exhibit a polygonal shape when viewed from the rotation axis direction dr1.

(5-11) Modification K
In the above embodiment, the present invention has been applied to a heat source side fan 30, which is an axial fan that sends air in the axial direction and is a so-called propeller fan. However, the model and type of the blower to which the present invention is applied can be appropriately changed according to the design specifications and the installation environment. For example, the application target of the present invention is not necessarily limited to a propeller fan, and may be another fan (for example, a turbo fan). Further, the application target of the present invention is not necessarily limited to the axial flow fan, and as long as the technical idea of the invention can be applied, the centrifugal fan that sends wind in the centrifugal direction with respect to the axial flow direction and the axial flow direction. It may be a mixed flow fan that sends wind in an oblique direction, a cross flow fan that sends wind in a direction different from the suction direction, or the like.

(5-12) Modification L
The configuration of the refrigerant circuit RC in the above embodiment can be appropriately changed according to the installation environment and design specifications. Specifically, in the refrigerant circuit RC, a part of the circuit element may be replaced with another device, or may be omitted as appropriate when it is not always necessary. Further, the refrigerant circuit RC may include equipment and a refrigerant flow path (not shown in FIG. 1).

(5-13) Modification M
In the above embodiment, the present invention has been applied to the heat source side fan 30. However, the present invention can be appropriately applied to blowers other than the heat source side fan 30. For example, the technical idea of the present invention may be applied to the user fan 31.

Further, in the above embodiment, the present invention has been applied to a blower included in a freezing device 100 that cools a target space S1 such as in a low temperature warehouse, in a shipping container, or in a store showcase. The present invention can also be applied to a blower included in another freezing device having a refrigerant circuit. For example, the present invention performs a refrigerating apparatus for heating or retaining heat in the target space S1 (that is, a refrigerating apparatus in which the heat source side heat exchanger 12 functions as a refrigerant evaporator or a heater), cooling of a living space or a vehicle, and the like. This may be applied to a blower included in an air conditioning system, a hot water supply device, a heat pump chiller, or the like that realizes air conditioning.

The present invention can also be applied to a blower included in a device other than the refrigerating device. For example, the present invention may be applied to a blower included in an air conditioner such as an air purifier, a humidifier, or a ventilation device. Further, for example, the present invention may be applied to a blower included in various devices such as a vacuum cleaner and a hair dryer.

(5-14) Modification N
In the above embodiment, the drive source of the heat source side fan 30 is a motor (heat source side fan motor M30). However, the drive source of the blower to which the present invention is applied is not necessarily limited to the motor, and can be appropriately changed according to the design specifications and the installation environment. For example, the drive source of the blower may be an engine.

The present invention can be used in a blower or a refrigerating apparatus including a blower.

12: Heat source side heat exchanger (heat exchanger)
30: Heat source side fan (blower)
40: Casing 41: Partition plate 50: Fan rotor 51: Core part 52: Bearing part 53: Side part 55: Blade (wing)
60, 60a: Shroud (ring part)
61: First stretched part (first part)
62: Second stretched part (second part)
63, 63a: Third stretched portion (third portion)
64: Fourth extension 65: Bell mouth (rectifying member)
66: Bellmouth windward end (rectifying member end)
70: Front plate 70a: Opening 100: Refrigerating device 121: Heat transfer tube 141: First flow path 142: Second flow path 611: First extension end (first end)
621: Second stretched end (second end)
631: Third stretched end 641: Fourth stretched end A1: Rotation axis C1: Gap D1: Distance (first distance)
F1: Outside air flow F2: Inside air flow Fa: Primary side air Fb: Secondary side air Fb1: Blow-out air Fb2: Backflow air H1: Suction port H2: Blowout L1, L1': Dimensions (first dimension)
M30: Heat source side fan motor (drive source)
P1: Virtual point RC: Refrigerant circuit S1: Target space S2: Heat source side heat exchanger accommodation space dr1: Rotation axis direction dr2: Radial direction

International Publication 2015/125486

Claims (7)

The core unit (51) connected to the drive source (M30) and
A plurality of blades (55) extending radially from the core portion when viewed from the rotation axis (A1) direction (dr1), and
A ring portion (60 ) connected to the tip of each blade on the outer side in the radial direction (dr2) of the blade and having a ring shape when viewed from the direction of the rotation axis.
A rectifying member (65), which is a cylindrical member arranged at a distance from the ring portion in the radial direction and extending in the direction of the rotation axis, for rectifying air sent by the blades.
With
The ring portion
The rotation includes the first end portion (611) located so as to overlap the rectifying member end portion (66), which is the windward end portion of the rectifying member when viewed from the radial direction, and the rotation inside the rectifying member in the radial direction. Part 1 (61) extending in the axial direction and
The first end portion (621) which is located at a distance from the rectifying member end portion in the rotation axis direction and overlaps with the rectifying member when viewed from the rotation axis direction, is connected to the first end portion, and is connected to the first end portion. The second part (62) extending in the radial direction to the two ends,
A third portion ( 63 ) connected to the second end portion and extending radially outside the rectifying member end portion in the radial direction.
Have,
The second end is positioned so as to overlap with a virtual point (P1) located at a position where the end of the rectifying member is linearly extended to the windward side in the direction of the rotation axis.
The first dimension (L1 ), which is the radial length of the third part, is 0.5 times or more the first distance (D1), which is the linear distance between the end of the rectifying member and the virtual point. ,
Blower (30). The core unit (51) connected to the drive source (M30) and
A plurality of blades (55) extending radially from the core portion when viewed from the rotation axis (A1) direction (dr1), and
A ring portion (60a ) connected to the tip of each blade on the outer side in the radial direction (dr2) of the blade and having a ring shape when viewed from the direction of the rotation axis.
A rectifying member (65), which is a cylindrical member arranged at a distance from the ring portion in the radial direction and extending in the direction of the rotation axis, for rectifying air sent by the blades.
With
The ring portion
The rotation includes the first end portion (611) located so as to overlap the rectifying member end portion (66), which is the windward end portion of the rectifying member when viewed from the radial direction, and the rotation inside the rectifying member in the radial direction. Part 1 (61) extending in the axial direction and
The second end portion (621) which is located at a distance from the rectifying member end portion in the rotation axis direction and overlaps with the rectifying member when viewed from the rotation axis direction, is connected to the first end portion, and the first portion is connected . The second part (62) extending to the second end and
A third portion ( 63a ) connected to the second end portion and extending radially outside the end portion of the rectifying member.
Have,
The second end portion is positioned so as to overlap with a virtual point (P1) located at a location where the end portion of the rectifying member is linearly extended to the windward side along the direction of the rotation axis.
The first dimension (L1' ), which is the radial length of the third part, is 0.5 times or more the first distance (D1), which is the linear distance between the end of the rectifying member and the virtual point. is there,
Blower (30). The third portion extends along the radial direction outside the rectifying member end in the radial direction, and then extends along the rotation axis direction.
The end portion of the rectifying member is located inside the third portion in the radial direction and overlaps with the third portion when viewed from the radial direction.
The blower (30) according to claim 2. The rectifying member is a bell mouth arranged on the leeward side of the wing.
The blower (30) according to any one of claims 1 to 3. The first distance is 5 mm or more and 15 mm or less .
The first dimension is 4 mm or more.
The blower (30) according to any one of claims 1 to 4. An axial fan that sends air in the direction of the rotation axis.
The blower (30) according to any one of claims 1 to 5. The blower (30) according to any one of claims 1 to 6, and the blower (30).
A heat exchanger (12) that includes a heat transfer tube through which the refrigerant flows and exchanges heat between the air flow generated by the blower and the refrigerant.
(100).

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