JP6095036B2 - Air conditioner unit - Google Patents

Description

  The present invention relates to an air conditioner unit that passes an airflow generated by rotation of a fan through a heat exchanger.

  In the top blow type outdoor unit of the air conditioner, heat exchange between the outside air and the refrigerant is performed by passing the air flow generated by the rotation of the fan through the heat exchanger. If the velocity distribution (wind velocity distribution) of the airflow passing through the heat exchanger is biased, the heat exchange efficiency in the heat exchanger will be reduced.

  Conventionally, in order to reduce the deviation of the wind speed distribution in the heat exchanger, the fin pitch of the lower heat exchanger far from the fan is made larger than the fin pitch of the upper heat exchanger close to the fan, so that the lower heat 2. Description of the Related Art An air conditioner top-blowing outdoor unit in which the ventilation resistance of an exchanger is smaller than the ventilation resistance of an upper heat exchanger is known (see Patent Documents 1 to 3).

  Further, conventionally, the pipe diameter of the lower heat exchanger is made smaller than the pipe diameter of the upper heat exchanger (see Patent Documents 1 and 4), or the fin shape or the number of rows of the upper and lower heat exchangers are mutually equal. There has also been proposed an air blower top blow type outdoor unit in which the ventilation resistance of the lower heat exchanger is made smaller than the ventilation resistance of the upper heat exchanger by making it different (see Patent Documents 2 and 4).

JP 2006-153332 A JP 2006-71162 A JP-A-4-116384 JP 2005-249255 A

  In an air conditioner top-blowing outdoor unit, when the unit is viewed along the axis of the fan, the range in which the heat exchanger is arranged and the range in which the heat exchanger is not arranged in the rotation direction of the fan Exists. A wall panel for preventing the passage of wind is arranged in a range where no heat exchanger is arranged. Therefore, in the top blow type outdoor unit of the air conditioner, when the fan rotates, the air flow is supplied into the unit from the range where the heat exchanger is arranged, but the unit from the range where the heat exchanger is not arranged There is no supply of airflow to the inside. Thereby, in the top blow type outdoor unit of the air conditioner, an uneven wind speed distribution occurs in the rotation direction of the fan. If there is a deviation in the wind speed distribution and airflow disturbance around the fan, the fluctuation of the airflow around the blade becomes strong while the fan blade moves, and vibration and energy loss increase.

  In a conventional air conditioner top blow type outdoor unit, when the unit is viewed along the axis of the fan, the lower heat exchanger range is the same as the upper heat exchanger range or the upper heat exchanger range. Therefore, the deviation of the wind speed distribution in the rotation direction of the fan becomes large even in a region close to the fan. Therefore, in the conventional air conditioner top-blowing outdoor unit, noise and energy loss due to vibration when the fan rotates are increased. On the other hand, when the range of the heat exchanger arranged on the side surface of the unit is expanded in the fan rotation direction, the deviation of the wind speed distribution in the fan rotation direction is reduced, but the maintenance work for the devices in the unit becomes difficult.

  The present invention has been made in order to solve the above-described problems. An air conditioner unit capable of reducing noise and improving energy efficiency and facilitating maintenance work is provided. The purpose is to obtain.

  An air conditioner unit according to the present invention includes a fan that rotates about an axis, and a heat exchanger that is disposed on a virtual setting plane that is disposed at a position shifted from the fan in the axial direction of the fan and that surrounds the axis. The heat exchanger is divided into a plurality of heat exchanging portions respectively present in a plurality of regions aligned in the axial direction of the fan, and the direction along the virtual setting plane in a plane perpendicular to the axis is set as the virtual setting plane. In the circumferential direction, the length of each heat exchanging part in the circumferential direction of the virtual setting surface is longer as the heat exchanging part exists in a region near the fan.

  According to the air conditioner unit of the present invention, the deviation of the wind speed distribution in the fan rotation direction can be suppressed around the fan, and noise can be reduced and energy efficiency can be improved. Moreover, the range in which the heat exchange part does not exist can be secured, and the maintenance work can be facilitated.

It is a perspective view which shows the air conditioner unit by Embodiment 1 of this invention. It is a perspective view which shows a part of air blower of FIG. 1, a heat exchanger, and a housing | casing. It is a top view which shows an outdoor unit when it sees along the axial direction of the fan of FIG. It is a perspective view which shows the outdoor unit for demonstrating each circumferential direction length of each heat exchange part of FIG. It is a perspective view which shows the outdoor unit for demonstrating the wind speed distribution in each heat exchange part of FIG. FIG. 6 is a sectional view taken along a plane VI in FIG. 5. FIG. 6 is a cross-sectional view along the plane VII in FIG. 5. It is typical sectional drawing along the plane VIII of FIG. It is a principal part perspective view which shows the outdoor unit by Embodiment 2 of this invention. FIG. 10 is a sectional view taken along a plane X in FIG. 9. It is sectional drawing along the plane XI of FIG. It is a principal part perspective view which shows the outdoor unit by Embodiment 3 of this invention. It is typical sectional drawing along the plane XIII of FIG. It is a principal part perspective view which shows the outdoor unit by Embodiment 4 of this invention. It is a schematic diagram which shows each fin in the heat exchange part of FIG. It is a principal part perspective view which shows the outdoor unit by Embodiment 5 of this invention. It is sectional drawing along the plane XVII of FIG. It is sectional drawing which shows the other example of the heat exchange panel of the outdoor unit by Embodiment 5 of this invention. It is sectional drawing which shows the other example of the heat exchange panel of the outdoor unit by Embodiment 5 of this invention. It is sectional drawing which shows the other example of the heat exchange panel of the outdoor unit by Embodiment 5 of this invention. It is a principal part perspective view which shows the outdoor unit by Embodiment 6 of this invention. FIG. 22 is a cross-sectional view taken along a plane XXII in FIG. 21. It is sectional drawing which shows the other example of the heat exchange panel of the outdoor unit by Embodiment 6 of this invention. It is a principal part perspective view which shows the outdoor unit by Embodiment 7 of this invention. It is a principal part perspective view which shows the outdoor unit for demonstrating each circumferential direction length of each heat exchange part of FIG. It is a principal part perspective view which shows the outdoor unit by Embodiment 8 of this invention. It is typical sectional drawing along the plane XXVII of FIG. It is a principal part perspective view which shows the outdoor unit by Embodiment 9 of this invention. FIG. 29 is a schematic cross-sectional view along a plane XXIX in FIG. 28.

Preferred embodiments of the present invention will be described below with reference to the drawings.
Embodiment 1 FIG.
1 is a perspective view showing an air conditioner unit according to Embodiment 1 of the present invention. In the figure, an air conditioner constitutes a refrigeration cycle by circulating a refrigerant between an indoor unit and an outdoor unit (air conditioner unit) 1. The outdoor unit 1 includes a housing 2 and an in-unit device 3 accommodated in the housing 2.

  The housing 2 includes a bottom plate 21, a top plate 22 positioned above the bottom plate 21, a plurality of support pillars 23 that are fixed to the outer periphery of the bottom plate 21 and support the top plate 22, the bottom plate 21, and the top plate A plurality of side panels 24 that form the side surfaces of the housing 2 are provided between the two. In this example, the shapes of the bottom plate 21 and the top plate 22 are substantially square, and four support pillars 23 are fixed to the four corners of the bottom plate 21 and the top plate 22. Therefore, in this example, the side surface of the housing 2 is formed by the four side panels 24.

  The in-unit device 3 includes a blower 31, a refrigeration cycle device 32 through which a refrigerant flows, and a drive control device (not shown) that controls driving of the blower 31 and the refrigeration cycle device 32. The refrigeration cycle equipment 32 includes a heat exchanger 321, a compressor, a solenoid valve, and a heat transfer tube (refrigerant tube) that are elements for configuring the refrigeration cycle.

  Here, FIG. 2 is a perspective view showing a part of the blower 31, the heat exchanger 321 and the housing 2 of FIG. The blower 31 includes a fan 311 that rotates about an axis A along the height direction of the outdoor unit 1, and a fan motor (drive unit) 312 that is connected to the fan 311 and generates a driving force that rotates the fan 311. doing.

  The fan 311 is arranged so as to be shifted upward with respect to the refrigeration cycle apparatus 32 in the direction along the axis A (the axial direction of the fan 311). The fan 311 is a propeller fan having a boss 313 arranged coaxially with the axis A and a plurality (four in this example) of blades 314 provided on the outer periphery of the boss 313. Each wing 314 is arranged away from each other in the circumferential direction of the boss 313. The fan motor 312 is disposed below the fan 311.

  In the heat exchanger 321, a plurality (two in this example) of regions 41 and 42 arranged in the direction along the axis A are set. In this example, the regions 41 and 42 are arranged in this order in the direction away from the fan 311. The heat exchanger 321 is divided into a plurality of heat exchange units 321a and 321b existing in the regions 41 and 42, respectively. Thereby, in the heat exchanger 321, the heat exchanging part 321 a existing in the area 41 is arranged closer to the fan 311 than the heat exchanging part 321 b existing in the area 42. In this example, the size of the region 41 is larger in the direction along the axis A than the size of the region 42.

  FIG. 3 is a top view showing the outdoor unit 1 when viewed along the axial direction of the fan 311 in FIG. 2. FIG. 4 is a perspective view showing the outdoor unit 1 for explaining the respective circumferential lengths of the heat exchange parts 321a and 321b of FIG. The heat exchanger 321 is disposed around the axis A. Moreover, the heat exchanger 321 is arrange | positioned on the virtual setting surface B surrounding the perimeter of the axis line A, as shown in FIG. The virtual setting plane B is a plane parallel to the axis A. Further, when the heat exchanger 321 is viewed in the direction along the axis A (the axial direction of the fan 311), the virtual setting surface B appears as an endless encircling line surrounding the axis A (FIG. 3). The virtual setting plane B is provided with a plurality of plane portions B1 to B4 that overlap each of the sides of the polygon surrounding the entire circumference of the axis A. In this example, four plane portions B1 to B4 of the virtual setting surface B are located on each of the sides of the quadrangle corresponding to the four side panels 24 of the housing 2. Among the refrigeration cycle devices 32, some devices (for example, a compressor, a solenoid valve, etc.) excluding the heat exchanger 321 are arranged inside the virtual setting plane B.

  Assuming that the direction along the virtual setting surface B in the plane perpendicular to the axis A is the circumferential direction of the virtual setting surface B, the lengths La and Lb of the heat exchange portions 321a and 321b in the circumferential direction of the virtual setting surface B As shown in FIG. 4, the heat exchange part existing in the region near the fan 311 is longer. That is, when the heat exchanger 321 is viewed in the direction along the axis A, the length La of the heat exchange unit 321a existing in the region 41 is longer than the region 41 in the region 42 farther from the fan 311. It is longer in the direction along the virtual setting plane B than the length of 321b (La> Lb). In this example, when the heat exchanger 321 is viewed in the direction along the axis A, the positions of the respective one end portions of the heat exchanging portions 321a and 321b coincide with each other in the direction along the virtual setting plane B. The positions of the other end portions of 321a and 321b are different from each other.

  Each heat exchanging section 321a, 321b is provided in each heat transfer tube (refrigerant tube) arranged at intervals, and heat radiation arranged at intervals in the length direction of the heat transfer tubes. Each having a plurality of fins. In each of the heat exchange units 321a and 321b, heat exchange is performed between the refrigerant and the outside air while the refrigerant sequentially passes through the heat transfer tubes. Each of the heat exchange units 321a and 321b may include a plurality of heat transfer tubes arranged at intervals from each other and a plurality of fins arranged in a waveform between the heat transfer tubes.

  Each side panel 24 of the housing 2 collectively surrounds the axis A and the virtual setting surface B. In each of the regions 41 and 42, a range in which the heat exchange units 321a and 321b exist and a range in which the heat exchange units 321a and 321b do not exist are generated in the rotation direction C (FIG. 3) of the fan 311. . In each side panel 24 of the housing 2, a portion covering a range where the heat exchange portions 321 a and 321 b exist is a panel ventilation portion 241 (FIG. 1) through which air (airflow) passes, and the heat exchange portions 321 a and 321 b. A portion covering a range where no air is present is a panel shielding portion 242 that prevents passage of wind (airflow). Therefore, at least one of the side panels 24 has the panel shielding part 242, and the panel shielding part 242 covers a range where the heat exchange parts 321a and 321b do not exist. In the panel ventilation part 241, as shown in FIG. 1, the grating | lattice 243 is provided in opening.

  The range in which the heat exchanger 321 does not exist in the rotational direction of the fan 311 is wider in the regions 41 and 42 that are farther from the fan 311 in the direction along the axis A. A part of the devices (for example, a compressor, a solenoid valve, and the like) disposed inside the virtual setting surface B is disposed in a region 42 that is farther from the fan 311 than the region 41 that is closest to the fan 311.

  As shown in FIG. 1, a blowout port 221 is provided at the center of the top plate 22. A bell mouth 222 that surrounds the outlet 221 is fixed on the top surface of the top plate 22. The fan 311 is disposed inside the bell mouth 222. The bell mouth 222 is provided with a net 223 that covers the opening of the bell mouth 222.

  In the outdoor unit 1, when the fan 311 rotates, as shown by an arrow V in FIG. 1, the fan 311 enters the housing 2 from the side surface of the housing 2, and passes from the inside of the housing 2 to the outside of the housing 2 through the outlet 221. A wind (airflow) is generated. Accordingly, the outdoor unit 1 is a so-called top blow type outdoor unit. The wind generated by the rotation of the fan 311 enters the casing 2 through the panel ventilation portion 241 of each side panel 24, passes through the heat exchanger 321, and then exits the casing 2 from the outlet 221. In the heat exchanger 321, heat is exchanged between the refrigerant passing through the heat transfer tube and the outside air by the wind from the panel ventilation portion 241 of the side panel 24 passing through the heat exchanger 321. In the range where the panel shielding part 242 of the side panel 24 is disposed, the inflow of wind from the side surface of the housing 2 into the housing 2 is prevented.

  FIG. 5 is a perspective view showing the outdoor unit 1 for explaining the wind speed distribution in each of the heat exchange units 321a and 321b of FIG. 6 is a cross-sectional view taken along the plane VI of FIG. 5, and FIG. 7 is a cross-sectional view taken along the plane VII of FIG. Of each region 41, 42, the airflow Va passing through the heat exchanging part 321 a existing in the region 41 close to the fan 311 is more than the airflow Vb passing through the heat exchanging part 321 b existing in the region 42 farther from the fan 311 than the region 41. Also, the fan 311 flows into the housing 2 from a wide range in the rotation direction. Therefore, in the region 41 close to the fan 311, the deviation of the velocity distribution of the air sucked into the housing 2 from the side surface of the housing 2 (suction air velocity distribution) is larger in the rotation direction of the fan 311 than in the region 42 far from the fan 311. It is getting smaller. Thereby, when the fan 311 rotates, the deviation of the wind speed distribution in the rotation direction of the fan 311 is reduced around the fan 311, and the fluctuation of the airflow generated in the blade 314 is reduced.

  FIG. 8 is a schematic cross-sectional view along the plane VIII of FIG. FIG. 8 shows the wind speed distribution on the plane VIII of FIG. 2 at three locations where the distance from the fan 311 in the direction along the axis A is different from each other. In FIG. 8, among the three locations indicating the wind speed distribution, the location closest to the fan 311 and the location closest to the fan 311 are the locations in the area 41, and the location farthest from the fan 311 is the area. 42.

  Of the above three locations, the wind speed distribution V1 at the location farthest from the fan 311 is formed by the airflow Vb that has passed through the heat exchange section 321b that exists only on one side in the housing 2 of FIG. The wind speed distribution is quickly biased on the side closer to the portion 321b. However, the airflow Vb that has passed through the heat exchanging portion 321b flows upward toward the fan 311 in the housing 2, and the airflow Va that has passed through the heat exchanging portions 321a existing on both sides of the housing 2 in FIG. Mix. Thereby, as shown in FIG. 6, the deviation of the wind speed distribution is a place farthest from the fan 311 (wind speed distribution V1), a place second closest to the fan 311 (wind speed distribution V2), and a place closest to the fan 311 ( In the order of the wind speed distribution V3), it becomes weaker as the fan 311 is approached. That is, when the air flow Vb flowing toward the fan 311 in the housing 2 is mixed with the air flow Va from the heat exchange unit 321a, the bias of the wind speed distribution is weakened, and the wind speed distribution V3 at the location closest to the fan 311 is The wind speed distribution is uniform in the rotation direction of the fan 311.

  In such an outdoor unit 1, the heat exchanger 321 is divided into a plurality of heat exchange portions 321 a and 321 b existing in a plurality of regions 41 and 42 arranged in the axial direction of the fan 311, and the circumferential direction of the virtual setting surface B Since the lengths La and Lb of the heat exchanging portions 321a and 321b are longer for the heat exchanging portion existing in the region close to the fan 311, the deviation of the wind speed distribution in the rotation direction of the fan 311 is reduced. Can be reduced around. Thereby, the fluctuation of the airflow in the blades 314 when the fan 311 rotates can be weakened, and the noise generated by the rotation of the fan 311 can be reduced. In addition, since energy loss of the fan 311 can be suppressed, the energy efficiency of the fan 311 can be improved. Furthermore, since the range in which the heat exchanger 321 does not exist in the rotation direction of the fan 311 can be secured widely in the area 42 away from the fan 311 among the areas 41 and 42, the equipment in the housing 2 Maintenance work can be facilitated. In addition, by arranging the device in the housing 2 in the region 42 that is farther from the fan 311 than in the region 41, the installation space for the device in the housing 2 can be more reliably secured and It is possible to reduce the influence of the equipment in the housing 2 on the deviation of the wind speed distribution in the case.

Embodiment 2. FIG.
FIG. 9 is a perspective view showing a main part of an outdoor unit 1 according to Embodiment 2 of the present invention. 10 is a cross-sectional view taken along the plane X in FIG. 9, and FIG. 11 is a cross-sectional view taken along the plane XI in FIG. Of each of the regions 41 and 42, the heat exchanging part 321a existing in the region 41 closest to the fan 311 is present in all of a plurality (four in this example) of the plane portions B1 to B4 provided on the virtual setting surface B. Has been placed. That is, when the outdoor unit 1 is viewed in the direction along the axis A, the heat exchanging part 321a is arranged on all sides of the polygon (in this example, a rectangle) surrounding the axis A as shown in FIG. Has been.

  As shown in FIG. 10, the heat exchanging part 321a is continuously arranged from one end of the heat exchanging part 321a along the circumferential direction of the virtual setting surface B and reaches the other end of the heat exchanging part 321a. A space between one end and the other end of the heat exchanging portion 321a in the circumferential direction of the virtual setting surface B (that is, a range in which the heat exchanging portion 321a does not exist in the region 41 in the rotation direction of the fan 311) is possible. It is as narrow as possible.

  The heat exchanging part 321b existing in the area 42 farther from the fan 311 than the area 41 is arranged in the remaining plane parts B1 to B3 excluding any of the plane parts B1 to B4 in the virtual setting plane B. Similarly to the heat exchanging part 321a, the heat exchanging part 321b is also arranged continuously from one end of the heat exchanging part 321b along the circumferential direction of the virtual setting surface B, as shown in FIG. 11, and the heat exchanging part 321b. To the other end. In this example, when the outdoor unit 1 is viewed along the axial direction of the fan 311, the positions of the one end portions of the heat exchanging portions 321 a and 321 b coincide with each other, and the other end portions of the heat exchanging portions 321 a and 321 b The positions are different from each other.

  In the heat exchanger 321, when viewed in the circumferential direction of the virtual setting surface B, the length of the heat exchange part 321 a is longer than the length of the heat exchange part 321 b. Therefore, the airflow Va passing through the heat exchanging part 321a close to the fan 311 is larger than the airflow Vb passing through the heat exchanging part 321b farther from the fan 311 than the heat exchanging part 321a from a wider range in the rotation direction of the fan 311. Will flow in. Other configurations are the same as those in the first embodiment.

  In such an outdoor unit 1, when the virtual setting surface B is viewed in the direction along the axis A, a plurality of plane portions B <b> 1 to B <b> 4 that respectively overlap each side of the polygon surrounding the axis A are on the virtual setting surface B. Among the regions 41 and 42, the heat exchanging part 321 a existing in the region 41 closest to the fan 311 among the regions 41 and 42 is disposed in all of the planar portions B1 to B4. In the region 41 closest to the fan 311, the deviation of the range of the heat exchanging part 321 a can be reduced in the rotation direction of the fan 311. As a result, it is possible to further reduce the deviation of the wind speed distribution in the rotation direction of the fan 311 around the fan 311 and to further suppress noise during rotation of the fan 311 and improve energy efficiency. .

Embodiment 3 FIG.
FIG. 12 is a perspective view showing a main part of an outdoor unit 1 according to Embodiment 3 of the present invention. FIG. 13 is a schematic cross-sectional view along the plane XIII of FIG. Of each of the regions 41 and 42, the heat exchanging part 321 a existing in the region 41 closest to the fan 311 has a plurality of heat exchange panels 322 arranged so as to overlap each other with the axis A inside. Ventilation resistance (pressure loss) ΔP [Pa] of the airflow Va passing through the heat exchanging part 321a existing in the region 41 closest to the fan 311 is the number of columns of the heat exchanging panels 322 in the heat exchanging part 321a. By adjusting the circumferential direction, the virtual setting surface B is made uniform in the circumferential direction. In this example, the number of rows of the heat exchange panels 322 in the heat exchange unit 321a is the same in the circumferential direction of the virtual setting surface B. That is, in the heat exchange part 321a, the number of rows of the heat exchange panels 322 is the same number (in this example, two rows) at any position in the circumferential direction of the virtual setting surface B. Other configurations are the same as those in the first embodiment.

  In such an outdoor unit 1, the ventilation resistance ΔP in the heat exchanging portion 321 a existing in the region 41 closest to the fan 311 among the regions 41 and 42 is uniform in the circumferential direction of the virtual setting surface B. Further, it is possible to further reduce the deviation of the ventilation distribution in the rotation direction of the fan 311 around the fan 311. Further, it is possible to further suppress noise during rotation of the fan 311 and improve energy efficiency.

  Moreover, in the heat exchange part 321a which exists in the area | region 41 nearest to the fan 311 among each area | region 41 and 42, since the number of rows of the heat exchange panel 322 is the same about the circumferential direction of the virtual setting surface B, The ventilation resistance ΔP of the air flow Va passing through the heat exchanging portion 321a can be easily equalized in the circumferential direction of the virtual setting surface B.

Embodiment 4 FIG.
FIG. 14 is a perspective view showing a main part of an outdoor unit 1 according to Embodiment 4 of the present invention. FIG. 15 is a schematic diagram showing the fins 324 in the heat exchange section 321a of FIG. Among the regions 41 and 42, in the heat exchange part 321 a existing in the region 41 closest to the fan 311, a plurality of fins 324 provided in the heat transfer tube (refrigerant tube) through which the refrigerant passes are in the circumferential direction of the virtual setting surface B. They are arranged at a distance from each other. Each fin 324 is a plate arranged along the axis A perpendicular to the circumferential direction of the virtual setting plane B. By adjusting the spatial dimension (fin pitch) Fp between the fins 324 in the circumferential direction of the virtual setting surface B, the ventilation resistance ΔP [Pa] of the air flow Va passing through the heat exchange section 321a is about the circumferential direction of the virtual setting surface B. It is uniform. In this example, in the heat exchange part 321a, the fin pitch Fp is the same at any position in the circumferential direction of the virtual setting surface B. Other configurations are the same as those in the first embodiment.

  In such an outdoor unit 1, the fin pitch Fp in the heat exchange part 321a existing in the region 41 closest to the fan 311 among the regions 41 and 42 is the same at any position in the circumferential direction of the virtual setting surface B. Therefore, the airflow resistance ΔP of the airflow Va passing through the heat exchange part 321a can be easily equalized in the circumferential direction of the virtual setting plane B.

  In the above example, the fin pitch Fp in the heat exchange part 321a is made the same in the circumferential direction of the virtual setting surface B, thereby uniformizing the ventilation resistance ΔP in the heat exchange part 321a in the circumferential direction of the virtual setting surface B. However, by making the shape of each fin 324 in the heat exchange part 321a the same in the circumferential direction of the virtual setting surface B, the ventilation resistance ΔP in the heat exchange part 321a is made uniform in the circumferential direction of the virtual setting surface B. You may do it. For example, when the configuration of the heat exchange unit 321a is a configuration in which a plurality of heat transfer tubes are arranged at intervals in the circumferential direction of the virtual setting surface B, and corrugated fins are provided between the heat transfer tubes, You may make it make the shape of each fin the same about the circumferential direction of the virtual setting surface B by making the pitch between heat exchanger tubes the same about the circumferential direction of the virtual setting surface B.

Embodiment 5. FIG.
FIG. 16 is a perspective view showing a main part of an outdoor unit 1 according to Embodiment 5 of the present invention. FIG. 17 is a sectional view taken along a plane XVII in FIG. Of each of the regions 41 and 42, the heat exchange unit 321 a existing in the region 41 closest to the fan 311 has a heat exchange panel 322. In this example, the number of rows of the heat exchange panels 322 in the heat exchange section 321a is one row.

  The heat exchange panel 322 includes a plurality of heat transfer tubes (refrigerant tubes) 325 arranged at intervals in the direction along the axis A and arranged along the circumferential direction of the virtual setting surface B, and the circumference of the virtual setting surface B It has a plurality of fins 324 arranged in the direction at intervals from each other and provided in each heat transfer tube. Each fin 324 is disposed perpendicular to the circumferential direction of the virtual setting surface B and is disposed along the axis A. Each heat transfer tube 325 passes through each fin 324.

  The ventilation resistance ΔP [Pa] of the air flow Va passing through the heat exchanging portion 321a is adjusted by adjusting the cross-sectional shape and the cross-sectional size of each heat transfer tube 325 in the circumferential direction of the virtual setting surface B. Has been homogenized. In this example, the cross-sectional shape and the cross-sectional size of each heat transfer tube 325 are the same at any position in the circumferential direction of the virtual setting surface B. In this example, each heat transfer tube 325 is a circular tube having an outer diameter D. Other configurations are the same as those of the first embodiment.

  Thus, by making the cross-sectional shape and cross-sectional size of the heat transfer tube 325 in the heat exchanging portion 321a the same in the circumferential direction of the virtual setting surface B, the heat exchanging portion 321a in the circumferential direction of the virtual setting surface B It is possible to make the ventilation resistance ΔP uniform.

  In the above example, the cross-sectional shape of each heat transfer tube 325 is circular, but the cross-sectional shape of each heat transfer tube 325 may be flat (for example, rectangular). When the cross-sectional shape of each heat transfer tube 325 is rectangular, as shown in FIG. 18, the dimensions of the short side D1 and the long side D2 of the rectangular cross section are the same in each heat transfer tube 325, and the long side D2 of the rectangle is Each heat transfer tube 325 is arranged perpendicular to the direction along the axis A. Even in this case, the ventilation resistance ΔP in the circumferential direction of the virtual setting surface B can be made uniform in the heat exchanging portion 321a.

  Further, the number of rows of the heat exchange panels 322 in the heat exchange unit 321a may be a plurality of rows. In this case, the cross-sectional shape and cross-sectional size of each heat transfer tube 325 may be different for each heat exchange panel 322. For example, as shown in FIG. 19, the number of rows of heat exchange panels 322 in the heat exchange section 321a is two, the cross-sectional shape of each heat transfer tube 325 of one heat exchange panel 322 is circular, and the other heat The cross-sectional shape of each heat transfer tube 325 of the exchange panel 322 may be a rectangle.

  Further, in the heat exchange part 321a, a plurality of heat transfer tubes 325 having different cross-sectional shapes may be incorporated in the common heat exchange panel 322. For example, as shown in FIG. 20, a heat transfer tube 325 having a rectangular cross-sectional shape and a heat transfer tube 325 having a circular cross-sectional shape may be arranged side by side on a common heat exchange panel 322.

Embodiment 6 FIG.
FIG. 21 is a perspective view showing a main part of an outdoor unit 1 according to Embodiment 6 of the present invention. FIG. 22 is a sectional view taken along a plane XXII in FIG. Of each of the regions 41 and 42, the heat exchange unit 321 a existing in the region 41 closest to the fan 311 has a heat exchange panel 322. In this example, the number of rows of the heat exchange panels 322 in the heat exchange unit 321a is one row. In the heat exchange panel 322 in the heat exchange unit 321a, the heat transfer tubes 325 are arranged at intervals in the direction along the axis A. By adjusting the center-to-center distance (heat transfer tube pitch) Dp of each heat transfer tube 325 in the circumferential direction of the virtual setting surface B, the ventilation resistance ΔP [Pa] of the air flow Va passing through the heat exchange part 321a is Uniform in the direction. In this example, the center-to-center distance (heat transfer tube pitch) Dp of each heat transfer tube 325 is the same in the circumferential direction of the virtual setting surface B in the heat exchange unit 321a. Moreover, in this example, the cross-sectional shape of each heat exchanger tube 325 is circular. Other configurations are the same as those of the fifth embodiment.

  As described above, by making the heat transfer tube pitch Dp in the heat exchanging portion 321a existing in the region 41 closest to the fan 311 the same in the circumferential direction of the virtual setting surface B, the heat exchanging portion 321a has the circumference of the virtual setting surface B. It is possible to make the ventilation resistance ΔP in the direction uniform.

  In the above example, the cross-sectional shape of each heat transfer tube 325 is circular. However, as shown in FIG. 23, the cross-sectional shape of each heat transfer tube 325 may be flat (for example, rectangular).

Embodiment 7 FIG.
FIG. 24 is a perspective view showing a main part of an outdoor unit 1 according to Embodiment 7 of the present invention. FIG. 25 is a main part perspective view showing the outdoor unit 1 for explaining the respective circumferential lengths of the heat exchanging parts 321a, 321b, 321c of FIG. In the present embodiment, the number of regions set in the heat exchanger 321 is three. That is, in the heat exchanger 321, three regions 41 to 43 arranged in the direction along the axis A are set. Of the areas 41 to 43, the area 41 is the area closest to the fan 311, the area 42 is the area closest to the fan 311, and the area 43 is the area farthest from the fan 311. The heat exchanger 321 is divided into three heat exchange units 321a, 321b, and 321c that exist in the regions 41 to 43, respectively.

  The lengths La, Lb, and Lc of the heat exchange portions 321a, 321b, and 321c in the circumferential direction of the virtual setting surface B are the heat exchange portions that exist in the region 43 farthest from the fan 311 among the regions 41 to 43. The heat exchange part 321b existing in the area 42 closest to the fan 311 and the heat exchange part 321a existing in the area 41 closest to the fan 311 are longer in this order (La> Lb> Lc). That is, the lengths La, Lb, and Lc of the heat exchanging portions 321 a, 321 b, and 321 c in the circumferential direction of the virtual setting surface B are longer as the heat exchanging portion exists in a region near the fan 311.

  In this example, the heat exchanging parts 321a and 321b existing in the area 41 closest to the fan 311 and the area 42 closest to the fan 311 are all in the four plane parts B1 to B4 of the virtual setting plane B. The heat exchange part 321c that is arranged and is present in the region 43 farthest from the fan 311 is arranged on the remaining three plane parts B1 to B3 excluding any of the four plane parts B1 to B4 of the virtual setting plane B. Yes. The compressor, the solenoid valve, and the heat transfer tube included in the refrigeration cycle device 32 are disposed in the regions 42 and 43 that are further away from the fan 311 than the region 41.

  In each of the regions 41 to 43, a range in which the heat exchange units 321a, 321b, and 321c exist and a range in which the heat exchange units 321a, 321b, and 321c do not exist are generated in the rotation direction of the fan 311. Of each side panel 24 of the housing 2, a portion covering a range where the heat exchange units 321 a, 321 b, and 321 c exist is a panel ventilation unit (not shown) through which wind (airflow) passes, and the heat exchange unit A portion covering a range where 321a, 321b, and 321c do not exist is a panel shielding portion 242 that blocks passage of wind (airflow). Other configurations are the same as those in the first embodiment.

  As described above, even if the number of regions arranged in the direction along the axis A is three and the heat exchangers 321 are divided into the three heat exchange units 321a, 321b, and 321c existing in the regions 41 to 43, respectively, By rotating the lengths La, Lb, and Lc of the heat exchanging portions 321 a, 321 b, and 321 c in the circumferential direction of the setting surface B as the heat exchanging portion existing in the region close to the fan 311, the rotation of the fan 311 is performed. The deviation of the wind speed distribution with respect to the direction can be reduced around the fan 311. As a result, noise during rotation of the fan 311 can be reduced and energy efficiency can be improved.

Embodiment 8 FIG.
FIG. 26 is a perspective view showing a main part of an outdoor unit 1 according to the eighth embodiment of the present invention. FIG. 27 is a schematic cross-sectional view along the plane XXVII in FIG. A drive control device 33 is accommodated in the housing 2. The drive control device 33 controls the drive of devices in the housing 2 (for example, a fan motor 312, a compressor motor, a solenoid valve, etc.). The drive control device 33 includes an electrical component that includes a circuit board and a box that houses the electrical component.

  The drive control device 33 is disposed in a region 42 that is farther from the fan 311 than the region 41. In addition, the drive control device 33 is arranged in a range where the heat exchanger 321 (that is, the heat exchange unit 321b) does not exist in the rotation direction of the fan 311. Further, the drive control device 33 is attached to the panel shielding part 242 of the side panel 24 in the housing 2. As a result, the drive control device 33 is covered with the panel shielding part 242. A heat sink 34 for cooling the circuit board and the like of the drive control device 33 is provided on the surface on the axis A side of the drive control device 33. Other configurations are the same as those of the second embodiment.

  In such an outdoor unit 1, the drive control device 33 housed in the housing 2 is disposed in the region 42 farther from the fan 311 than the region 41, and is provided in the panel shielding part 242 of the side panel 24. Therefore, the drive control device 33 can be protected from the environment (for example, wind and rain) outside the housing 2 by the panel shielding unit 242. Further, since the position of the drive control device 33 is away from the fan 311, the influence of the drive control device 33 on the wind speed distribution around the fan 311 can be reduced, and the drive control device 33 is placed in the housing 2. An increase in the deviation of the wind speed distribution due to the arrangement can be suppressed. Furthermore, since the drive control device 33 is disposed in the area 42 that is small in the range occupied by the heat exchanger 321, it is possible to easily secure an arrangement space for the drive control device 33 and the heat sink 34, and to the drive control device 33. Maintenance work can be facilitated.

Embodiment 9 FIG.
FIG. 28 is a perspective view showing a main part of an outdoor unit 1 according to the ninth embodiment of the present invention. FIG. 29 is a schematic cross-sectional view along the plane XXIX in FIG. The panel shield 242 of the side panel 24 is provided with an entrance 25 that allows access from outside the housing 2 to the inside of the housing 2. The entrance / exit 25 is located in a region 42 farther from the fan 311 than the region 41. Further, the panel shielding part 242 is provided with a lid 26 for opening and closing the entrance 25. The lid | cover 26 is comprised with the board which blocks | prevents passage of a wind (airflow). Other configurations are the same as those of the second embodiment.

  In such an outdoor unit 1, the entrance / exit 25 is provided in the panel shielding part 242 of the side panel 24, and the entrance / exit 25 is located in the region 42 farther from the fan 311 than the region 41. The influence of the entrance / exit 25 on the wind speed distribution can be reduced, and an increase in the bias of the wind speed distribution due to the provision of the entrance / exit 25 in the panel shielding part 242 of the side panel 24 can be suppressed. Moreover, since the entrance / exit 25 is provided in the panel shielding part 242 located in the area | region 42 where the range which the heat exchanger 32 occupies is small, it can make it easy to avoid the heat exchanger 321 and to ensure the magnitude | size of the entrance / exit 25. For example, maintenance work of heavy objects such as a compressor can be further facilitated.

  In each of the above embodiments, when the virtual setting plane B is viewed in the direction along the axis A, the four plane portions B1 to B4 that respectively overlap the square sides surrounding the entire circumference of the axis A are the virtual setting plane. Although provided in B, the polygon surrounding the entire circumference of the axis A is not limited to a quadrangle, and may be, for example, a triangle or a hexagon. In this case, the number of plane portions that overlap each side of the polygon is the same as the number of each side of the polygon.

  In the first to sixth, eighth, and ninth embodiments, the number of the regions 41 and 42 aligned in the direction along the axis A is two. However, the number of the regions aligned in the direction along the axis A is Three or more may be used.

  In the third to sixth embodiments, the configuration of the heat exchanging unit 321a existing in the region 41 closest to the fan 311 is applied to the configuration of the heat exchanging unit 321b existing in the region 42 farther from the fan 311 than the region 41. May be. In this way, not only in the heat exchanging part 321a but also in the heat exchanging part 321b, the airflow resistance in the circumferential direction of the virtual setting surface B can be made uniform, and the wind speed distribution around the fan 311 can be improved. The bias can be further reduced.

  The present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the present invention. Furthermore, the present invention can also be implemented by combining the above embodiments.

Claims (8)

A fan that rotates about an axis, and a heat exchanger that is disposed on a virtual setting surface that surrounds the axis, and is disposed at a position shifted from the fan in the axial direction of the fan.
The virtual setting surface is a surface parallel to the axis,
The heat exchanger is divided into three or more heat exchanging portions respectively present in three or more regions arranged in the axial direction of the fan,
When the direction along the virtual setting surface in the plane perpendicular to the axis is the circumferential direction of the virtual setting surface, the length of each heat exchange unit in the circumferential direction of the virtual setting surface is The air conditioner unit which becomes longer as the heat exchange part existing in the near area. A plurality of side panels surrounding the fan axis, and further comprising a housing for housing the fan and the heat exchanger;
At least one of the side panels has a panel shielding portion that prevents the passage of airflow,
The panel shielding portion covers a range where the heat exchanger does not exist in the rotation direction of the fan,
The panel shield is provided with an entrance that allows access from outside the housing to the inside of the housing,
The air conditioner unit according to claim 1, wherein the entrance / exit is located in the region farther from the fan than the region closest to the fan. The air conditioner unit according to claim 2, wherein the panel shielding unit is integrated over the three or more regions. When the virtual setting surface is viewed along the axial direction of the fan, the virtual setting surface is provided with a plurality of flat portions respectively overlapping each side of the polygon surrounding the axis,
The said heat exchange part which exists in the said area | region nearest to the said fan is arrange | positioned at all of each said plane part, when the said heat exchanger is seen along the axial direction of the said fan. The air conditioner unit according to claim 3.   The air conditioning according to any one of claims 1 to 4, wherein the ventilation resistance is uniform in the circumferential direction of the virtual setting surface in the heat exchange part existing in the region closest to the fan. Machine unit. The heat exchange part present in the region closest to the fan has a plurality of heat exchange panels arranged with the axis of the fan inward,
6. The air conditioner unit according to claim 5, wherein in the heat exchange unit existing in the region closest to the fan, the number of rows of the heat exchange panels is the same in the circumferential direction of the virtual setting surface. The heat exchange part existing in the region closest to the fan has a plurality of heat transfer tubes and a plurality of fins provided on the heat transfer tubes,
In the heat exchange part existing in the region closest to the fan, at least one of the shape of the fin, the pitch between the fins, the outer shape of the heat transfer tube, and the pitch between the heat transfer tubes is the virtual The air conditioner unit according to claim 5, which is the same in the circumferential direction of the setting surface. A plurality of side panels surrounding the fan axis, and further comprising a housing for housing the fan and the heat exchanger;
At least one of the side panels has a panel shielding portion that prevents the passage of airflow,
The panel shielding portion covers a range where the heat exchanger does not exist in the rotation direction of the fan,
The drive control device for controlling the drive of the device in the housing is attached to the panel shielding unit in the housing and is disposed in the region farther from the fan than the region closest to the fan. The air conditioner unit as described in any one of Claims 1-7.

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