[go: up one dir, main page]

WO2019198150A1 - Climatiseur - Google Patents

Climatiseur Download PDF

Info

Publication number
WO2019198150A1
WO2019198150A1 PCT/JP2018/015086 JP2018015086W WO2019198150A1 WO 2019198150 A1 WO2019198150 A1 WO 2019198150A1 JP 2018015086 W JP2018015086 W JP 2018015086W WO 2019198150 A1 WO2019198150 A1 WO 2019198150A1
Authority
WO
WIPO (PCT)
Prior art keywords
distance
centrifugal fan
heat exchanger
section
rotation axis
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2018/015086
Other languages
English (en)
Japanese (ja)
Inventor
惇司 河野
拓矢 寺本
栗原　誠
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to PCT/JP2018/015086 priority Critical patent/WO2019198150A1/fr
Priority to JP2020512973A priority patent/JP7055197B2/ja
Publication of WO2019198150A1 publication Critical patent/WO2019198150A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/20—Casings or covers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/30—Arrangement or mounting of heat-exchangers

Definitions

  • the present invention relates to an air conditioner equipped with a centrifugal fan.
  • Patent Document 1 describes a turbofan having an impeller having a main plate, a side plate, and a plurality of blades, and a mouth ring that forms a throttle toward a suction port of the impeller.
  • the partition wall around the mouth ring is provided with a backflow prevention ring whose tip edge reaches the vicinity of the side plate. This document describes that the noise of the fan can be reduced without reducing the efficiency of the fan by providing the above-described backflow prevention ring.
  • the ceiling-embedded indoor unit has a centrifugal fan and a heat exchanger arranged so as to surround the outer periphery of the centrifugal fan.
  • the main stream of air blown out from the centrifugal fan to the outer peripheral side passes through the heat exchanger and becomes conditioned air, which is supplied indoors.
  • a part of the air blown out from the centrifugal fan becomes a secondary flow that does not pass through the heat exchanger and flows backward toward the annular space formed on the outer peripheral side of the side plate.
  • a secondary vortex having an axial center along the circumferential direction of the centrifugal fan is generated in the annular space.
  • the turbo fan of Patent Document 1 When the turbo fan of Patent Document 1 is applied to a ceiling-embedded indoor unit, the annular space sandwiched between the mouth ring and the side plate is separated from the air path by the backflow prevention ring, so that secondary vortices are generated in the annular space. It can be suppressed from occurring. Further, in the region where the radial distance between the outer peripheral edge of the centrifugal fan and the heat exchanger is relatively short in the circumferential direction of the centrifugal fan, the radial distance between the backflow prevention ring and the heat exchanger is short. For this reason, even if a secondary vortex is formed in a space sandwiched between the backflow prevention ring and the heat exchanger, the vortex diameter of the secondary vortex can be reduced.
  • the present invention has been made to solve the above-described problems, and an object thereof is to provide an air conditioner that can improve the blowing efficiency of a centrifugal fan.
  • An air conditioner includes a centrifugal fan that rotates about a rotation axis, a heat exchanger that is disposed so as to surround an outer periphery of the centrifugal fan, and a suction side region and a blowout side region of the centrifugal fan.
  • a first partition that partitions, and a second partition that is provided at least partially in the circumferential direction around the rotation axis and extends from the first partition toward the centrifugal fan.
  • the partition wall has a first end portion supported by the first partition wall and a second end portion which is an end portion on the centrifugal fan side, and has a diameter around the rotation axis.
  • the distance between the outer peripheral edge of the centrifugal fan and the second end in the direction is the first distance
  • the distance between the outer peripheral edge and the heat exchanger in the radial direction is the second distance
  • a radial cross section parallel to the rotation axis is defined as a first radial cross section
  • a radial cross section that passes through the rotation axis and is parallel to the rotation axis and has the second distance longer than the second distance in the first radial cross section is a second diameter.
  • the first distance in the second radial cross section is longer than the first distance in the first radial cross section.
  • the present invention it is possible to prevent the mainstream flow from being obstructed by the secondary vortex in both the first radial cross section and the second radial cross section, and rotate the passing air speed of the heat exchanger. It can be made uniform in the axial direction. Therefore, since the pressure loss of the heat exchanger can be reduced, the blowing efficiency of the centrifugal fan can be improved.
  • FIG. 7 is a diagram schematically showing a VII-VII cross section of FIG. 6.
  • FIG. 7 is a diagram schematically showing a VIII-VIII cross section of FIG. 6.
  • FIG. 1 An air conditioner according to Embodiment 1 of the present invention will be described.
  • a ceiling-embedded indoor unit 100 of a packaged air conditioner is illustrated as an air conditioner.
  • FIG. 1 is an external view showing an installation mode when the air conditioner according to the present embodiment is viewed obliquely from below.
  • FIG. 2 is a side view showing the internal structure of the air conditioner according to the present embodiment.
  • the main part of the indoor unit 100 is embedded in a ceiling space above the ceiling 201.
  • the lower part of the indoor unit 100 faces the room 202 which is a space to be air-conditioned.
  • the main body 20 of the indoor unit 100 includes a main body top plate 5 having a rectangular shape in plan view, and four main body side plates 4 extending downward from four sides of the main body top plate 5.
  • the main body 20 is a box body in which the upper end of a rectangular tube body composed of four main body side plates 4 is closed by the main body top plate 5.
  • a decorative panel 6 is detachably attached to the main body 20 at a lower portion of the main body 20, that is, at a lower end of the rectangular tube body.
  • the main body top plate 5 is located above the ceiling 201, and the decorative panel 6 is located substantially on the same plane as the ceiling 201.
  • the indoor unit 100 has at least one inlet for sucking room air into the main body 20 and at least one outlet for blowing conditioned air from the main body 20 to the room 202.
  • a suction grill 7 is provided as a suction port of the indoor unit 100 at the center of the decorative panel 6. Above the suction grill 7, a filter 8 that removes dust sucked in from the suction grill 7 is provided.
  • the decorative panel 6 and the suction grille 7 each have a rectangular outer edge in plan view. In the region between the outer edge of the decorative panel 6 and the outer edge of the suction grill 7, a plurality of panel outlets 9 are provided as outlets of the indoor unit 100.
  • each panel outlet 9 is provided corresponding to the fact that each of the decorative panel 6 and the suction grille 7 has four outer edges.
  • the four panel outlets 9 are arranged along the sides of the decorative panel 6 and the suction grille 7.
  • the four panel outlets 9 are arranged so as to surround the suction grille 7.
  • Each panel outlet 9 is provided with a wind direction plate 13 for adjusting the air blowing direction.
  • a fan motor 2 is provided at the center inside the main body 20.
  • the fan motor 2 is attached to the lower surface of the main body top plate 5.
  • the output shaft of the fan motor 2 extends downward.
  • a centrifugal fan 1 that rotates about a rotation axis CL is connected to the output shaft of the fan motor 2.
  • a turbo fan is illustrated as the centrifugal fan 1.
  • the centrifugal fan 1 has a disk-shaped main plate 10 having a boss that is a fixed portion to the output shaft of the fan motor 2. Further, the centrifugal fan 1 has a side plate 11 that is disposed to face the main plate 10 and forms a suction air introduction wall of the centrifugal fan 1.
  • a plurality of blades 12 are provided between the main plate 10 and the side plate 11.
  • the centrifugal fan 1 When viewed parallel to the rotation axis CL, the centrifugal fan 1 has a circular outer peripheral edge.
  • a fan suction port 1 a serving as a suction port for the centrifugal fan 1 is formed at the center of the side plate 11.
  • a region on the upstream side of the fan suction port 1 a is a suction side region 30 of the centrifugal fan 1.
  • a fan air outlet 1 b serving as an air outlet of the centrifugal fan 1 is formed on the outer peripheral edge of the centrifugal fan 1.
  • the area on the downstream side of the fan outlet 1 b is the outlet area 31 of the centrifugal fan 1.
  • a bell mouth 14 that forms a suction air passage from the suction grill 7 toward the centrifugal fan 1 in the suction side region 30 is provided.
  • the bell mouth 14 is formed in a curved surface shape so that the diameter is reduced toward the downstream side.
  • the indoor unit 100 has a first partition wall 21 that partitions the suction side region 30 and the blowout side region 31 of the centrifugal fan 1.
  • the first partition wall 21 also serves as the bell mouth 14, but the first partition wall 21 may be provided separately from the bell mouth 14.
  • a heat exchanger 3 is provided in the blowout side region 31 on the radially outer side of the centrifugal fan 1 so as to surround the outer periphery of the centrifugal fan 1.
  • the heat exchanger 3 is accommodated in the main body 20 and is arranged on the air path in the main body 20.
  • the heat exchanger 3 constitutes a part of a refrigeration cycle circuit in which a refrigerant circulates, for example.
  • heat exchange between the internal fluid flowing through the inside and the air blown by the centrifugal fan 1 is performed.
  • the heat exchanger 3 has a plurality of fins arranged in the horizontal direction at predetermined intervals, and a heat transfer tube extending in the horizontal direction and penetrating the plurality of fins. .
  • a cooled or heated internal fluid for example, a refrigerant
  • a drain pan 16 that receives condensed water generated by cooling the indoor air by the heat exchanger 3 is disposed.
  • the drain pan 16 may also serve as the first partition wall 21.
  • the centrifugal fan 1 when the centrifugal fan 1 is rotationally driven by the fan motor 2, the air in the room 202 is sucked into the suction grille 7 and is removed by the filter 8.
  • the dust-removed air is guided by the bell mouth 14 and flows upward into the centrifugal fan 1 in the direction of the rotation axis CL.
  • the air that has flowed into the centrifugal fan 1 is blown out radially outward from the centrifugal fan 1.
  • the air blown out from the centrifugal fan 1 passes through the heat exchanger 3.
  • the air passing through the heat exchanger 3 is cooled or heated by heat exchange with the internal fluid. Thereby, the temperature or humidity of air is adjusted.
  • the air that has passed through the heat exchanger 3 changes its flow direction downward along the air path in the main body 20, and is blown out to the room 202 through the panel outlet 9.
  • a second partition wall 22 formed on the first partition wall 21 is provided.
  • the second partition wall 22 extends upward from the first partition wall 21 toward the side plate 11.
  • the second partition wall 22 may be formed on the bell mouth 14 or the drain pan 16.
  • the second partition wall 22 may be inclined with respect to the rotation axis CL.
  • the second partition 22 has a first end 22 a supported by the first partition 21 and a second end 22 b facing the side plate 11.
  • the second end 22b of the second partition 22 is an end away from the first partition 21 and is an end on the centrifugal fan 1 side.
  • 3 to 5 are perspective views showing examples of configurations of the heat exchanger 3, the centrifugal fan 1, the second partition wall 22, and the bell mouth 14 of the air conditioner according to the present embodiment.
  • the installed state means that the heat exchanger 3, the centrifugal fan 1, the second partition wall 22, and the bell mouth 14 (that is, the first partition wall 21) in the indoor unit 100 with the upside-down inverted are slanted.
  • a configuration viewed from above is shown.
  • only a part of the bell mouth 14 near the centrifugal fan 1 is shown in the axial direction.
  • the second partition wall 22 is provided on the entire circumference in the circumferential direction around the rotation axis CL of the centrifugal fan 1.
  • the second partition wall 22 has a quadrangular shape (for example, a square shape) surrounding the rotation axis CL.
  • the shape of the heat exchanger 3 when viewed in parallel with the rotation axis CL is a square shape
  • the four corners of the second partition wall 22 are circumferential with respect to the four corners of the heat exchanger 3. They are offset by about 45 °.
  • the second end 22b of the second partition wall 22 is disposed at a predetermined interval from the side plate 11 in the direction of the rotation axis CL so as not to contact the rotating centrifugal fan 1.
  • the distance in the rotation axis CL direction between the first end 22 a and the second end 22 b of the second partition 22, that is, the height of the second partition 22 depends on the shape of the side plate 11.
  • the second partition 22 differs depending on the circumferential position.
  • the second end 22b is located on the inner peripheral side with respect to the outer peripheral edge of the centrifugal fan 1 in at least part of the circumferential direction.
  • the second end 22b may be located on the inner peripheral side with respect to the outer peripheral edge of the centrifugal fan 1 over the entire periphery.
  • the example shown in FIG. 4 is different from the example shown in FIG. 3 in that the second partition 22 is provided only in a part of the circumferential direction around the rotation axis CL.
  • the second partition wall 22 is provided only in a portion where the radial distance between the outer peripheral edge of the centrifugal fan 1 and the heat exchanger 3 becomes relatively short in the circumferential direction. It is not provided in a portion where the distance becomes relatively long.
  • the second partition wall 22 is configured by four L-shaped portions 22c separated from each other when viewed in parallel with the rotation axis CL. The corners of the four L-shaped portions 22c are arranged so as to be shifted from the four corners of the heat exchanger 3 by about 45 ° in the circumferential direction.
  • the second end 22b When viewed in parallel with the rotation axis CL, the second end 22b is located on the inner peripheral side with respect to the outer peripheral edge of the centrifugal fan 1 in at least part of the circumferential direction.
  • the second end 22b may be located on the inner peripheral side with respect to the outer peripheral edge of the centrifugal fan 1 over the entire region.
  • FIG. 6 is a diagram illustrating a configuration in which the heat exchanger 3, the centrifugal fan 1, the second partition wall 22, and the bell mouth 14 illustrated in FIG. 3 are viewed in parallel with the rotation axis CL.
  • FIG. 6 the structure which looked at the heat exchanger 3, the centrifugal fan 1, the 2nd partition 22, and the bellmouth 14 from the downward direction in the installation state of the indoor unit 100 is shown.
  • the rotation direction of the centrifugal fan 1 is indicated by a thick arrow.
  • the distance between the outer peripheral edge 23 of the centrifugal fan 1 and the second end 22b of the second partition wall 22 in the radial direction around the rotation axis CL is defined as a first distance L1.
  • the first distance L1 is a positive value
  • the second end 22b is on the outer peripheral side with respect to the outer peripheral edge 23.
  • the first distance L1 is a negative value.
  • the distance between the outer peripheral edge 23 and the heat exchanger 3 in the radial direction around the rotation axis CL is defined as a second distance L2.
  • the second partition wall 22 is provided so that the first distance L1 varies depending on the circumferential position about the rotation axis CL.
  • the heat exchanger 3 is formed in a polygonal shape having a plurality of bent portions or curved portions when viewed in parallel with the rotation axis CL in order to ensure a large heat transfer area in the rectangular tube-shaped main body 20. ing.
  • the outer peripheral edge 23 of the centrifugal fan 1 is circular. For this reason, the second distance L2 also varies depending on the circumferential position about the rotation axis CL.
  • the second distance L2 decreases as the angle from the circumferential position A1 increases in the rotational direction of the centrifugal fan 1.
  • the first distance L1 decreases as the angle from the circumferential position A1 increases in the rotational direction of the centrifugal fan 1. That is, in the range of the circumferential position where the second distance L2 decreases as the angle increases in the rotation direction of the centrifugal fan 1, the first distance L1 decreases as the angle increases in the rotation direction of the centrifugal fan 1.
  • a range of circumferential positions is included.
  • the second distance L2 increases as the angle from the circumferential position A2 increases in the rotational direction of the centrifugal fan 1.
  • the first distance L1 increases as the angle from the circumferential position A2 increases in the rotational direction of the centrifugal fan 1. That is, in the range of the circumferential position where the second distance L2 increases as the angle increases in the rotational direction of the centrifugal fan 1, the first distance L1 increases as the angle increases in the rotational direction of the centrifugal fan 1.
  • a range of circumferential positions is included.
  • FIG. 7 is a diagram schematically showing a section VII-VII in FIG.
  • the section VII-VII is a radial section about the rotation axis CL. 7 and FIG. 8 to be described later show not only the heat exchanger 3, the centrifugal fan 1, the second partition wall 22, and the bell mouth 14, but also a cross section of the entire indoor unit 100.
  • the radial position of the second end 22b of the second partition wall 22 substantially coincides with the radial position of the outer peripheral edge 23 in the radial section shown in FIG.
  • the first distance L1 (not shown in FIG. 7) is substantially zero.
  • the second distance L2 is relatively short. That is, in this radial cross section, the distance (L1 + L2) between the heat exchanger 3 and the second end 22b is relatively short.
  • the vortex diameter of the secondary vortex 24 formed in the air path becomes small. For this reason, in the radial direction cross section shown in FIG.
  • FIG. 8 is a diagram schematically showing a section VIII-VIII in FIG.
  • a section VIII-VIII is a radial section about the rotation axis CL.
  • the second distance 22 is relatively longer because the second end 22 b of the second partition wall 22 is located on the inner peripheral side than the outer peripheral edge 23.
  • the second distance L2 is relatively long. That is, in this radial cross section, the distance (L1 + L2) between the heat exchanger 3 and the second end 22b is relatively long.
  • the second end 22 b is located on the inner peripheral side of the outer peripheral edge 23 in the radial cross section shown in FIG. 8. Therefore, a space 25 sandwiched between the side plate 11 and the bell mouth 14 is formed on the outer peripheral side of the second partition wall 22 and on the inner peripheral side of the outer peripheral edge 23.
  • the space 25 has a radial width equal to the first distance L1.
  • the secondary vortex 24 is formed away from the heat exchanger 3 and closer to the space 25, the vortex diameter of the secondary vortex 24 can be reduced.
  • the side plate 11 and the bell mouth 14 can restrict the expansion of the vortex diameter of the secondary vortex 24. For this reason, even in the radial cross section shown in FIG. 8, the mainstream flow can be prevented from being obstructed by the secondary vortex 24, and the passing air speed of the heat exchanger 3 can be made uniform in the direction of the rotation axis CL. it can. Therefore, since the pressure loss of the heat exchanger 3 can be reduced, the ventilation efficiency of the centrifugal fan 1 can be improved.
  • the second partition wall 22 is provided not only in the radial section shown in FIG. 7 but also in the radial section shown in FIG.
  • region 30 can be enlarged.
  • region 30 can be reduced. Therefore, since the pressure loss in the blowing side area
  • the third distance L3 in the radial cross section shown in FIG. It is shorter than the third distance L3 in the radial cross section shown. That is, the third distance L3 in each radial section is shorter as the radial section is longer in the first distance L1. Further, the third distance L3 in each radial cross section is shorter as the radial cross section is longer in the second distance L2. Furthermore, the third distance L3 in each radial section is shorter as the radial section in which the distance (L1 + L2) between the heat exchanger 3 and the second end 22b is longer.
  • the second end portion 22b is viewed in parallel with the rotation axis CL. It overlaps with the outer peripheral edge 23 of the centrifugal fan 1.
  • a radial cross section in which the third distance L3 is shorter than the distance (L1 + L2), the second end 22b is the outer peripheral edge 23 when viewed in parallel with the rotation axis CL. It is located on the inner circumference side.
  • the air conditioner according to the present embodiment includes the centrifugal fan 1 that rotates about the rotation axis CL, the heat exchanger 3 that is disposed so as to surround the outer periphery of the centrifugal fan 1, and the centrifugal fan.
  • a first partition wall 21 that separates the one suction side region 30 from the blowout side region 31, and at least part of the first partition wall 21 in the circumferential direction around the rotation axis CL, and from the first partition wall 21 toward the centrifugal fan 1.
  • an extended second partition wall 22 is an extended second partition wall 22.
  • the second partition 22 has a first end 22a supported by the first partition 21 and a second end 22b which is an end on the centrifugal fan 1 side.
  • the distance between the outer peripheral edge 23 of the centrifugal fan 1 and the second end 22b in the radial direction around the rotation axis CL is defined as a first distance L1
  • the outer peripheral edge 23 in the radial direction and the heat exchanger 3 are Is the second distance L2.
  • a radial cross section passing through the rotation axis CL and parallel to the rotation axis CL is defined as a first radial cross section (for example, a radial cross section shown in FIG. 7), and passing through the rotation axis CL and parallel to the rotation axis CL.
  • a radial cross section having a second distance L2 longer than the second distance L2 in the first radial cross section is defined as a second radial cross section (for example, the radial cross section shown in FIG. 8). .
  • the first distance L1 in the second radial cross section is longer than the first distance L1 in the first radial cross section.
  • the main flow can be prevented from being obstructed by the secondary vortex 24 in both the first radial cross section and the second radial cross section, and the passing wind speed of the heat exchanger 3 can be prevented.
  • the second end 22b when viewed in parallel with the rotation axis CL, the second end 22b is located on the inner peripheral side of the outer peripheral edge 23 over the entire circumference in the circumferential direction. Also good.
  • the distance between the first end 22a and the second end 22b in the axial direction parallel to the rotation axis CL is defined as a third distance L3.
  • the rotation axis CL at the circumferential position where the third distance L3 is longer than the sum of the first distance L1 and the second distance L2 (for example, the circumferential position of the radial section shown in FIG. 7), the rotation axis CL , The second end 22b may overlap the outer peripheral edge 23.
  • the second end 22 b may be located on the inner peripheral side with respect to the outer peripheral edge 23.
  • FIG. 9 is a diagram illustrating a configuration in which the heat exchanger 3, the centrifugal fan 1, the second partition wall 22, and the bell mouth 14 of the air conditioner according to the present embodiment are viewed in parallel with the rotation axis CL. 9, the structure which looked at the heat exchanger 3, the centrifugal fan 1, the 2nd partition 22, and the bell mouth 14 from the downward direction in the installation state of the indoor unit 100 is shown similarly to FIG.
  • symbol is attached
  • the first distance L1 between the outer peripheral edge 23 of the centrifugal fan 1 and the second end 22b is minimal at the circumferential position B1.
  • the circumferential position B2 is closest to the circumferential position B1 in the circumferential direction.
  • the circumferential position B1 is disposed at a position shifted from the circumferential position B2 in the circumferential direction.
  • the circumferential position B1 is positioned forward in the rotational direction of the centrifugal fan 1 with respect to the circumferential position B2.
  • the circumferential position B1 at which the first distance L1 is minimized is shifted in the circumferential direction from the circumferential position B2 at which the second distance L2 is minimized. It is arranged at the position.
  • the circumferential position B1 is positioned forward in the rotational direction of the centrifugal fan 1 with respect to the circumferential position B2. According to this configuration, the air path between the heat exchanger 3 and the second partition wall 22 can be prevented from abruptly shrinking in the rotation direction of the centrifugal fan 1, thereby suppressing an increase in pressure loss. Can do.
  • FIG. 10 is a diagram illustrating a configuration in which the heat exchanger 3, the centrifugal fan 1, the second partition wall 22, and the bell mouth 14 of the air conditioner according to the present embodiment are viewed in parallel with the rotation axis CL.
  • FIG. 10 the structure which looked at the heat exchanger 3, the centrifugal fan 1, the 2nd partition 22, and the bell mouth 14 from the downward direction in the installation state of the indoor unit 100 is shown similarly to FIG.
  • symbol is attached
  • the first distance L1 between the outer peripheral edge 23 of the centrifugal fan 1 and the second end 22b is minimal at the circumferential position C1.
  • the increase rate of the first distance L1 per angle from the circumferential position C1 to the rotation direction of the centrifugal fan 1 is the counter rotation direction of the centrifugal fan 1 from the circumferential position C1 (FIG. 10). (Clockwise direction) of the first distance L1 per angle is smaller than the increase rate.
  • the second distance L2 between the outer peripheral edge 23 and the heat exchanger 3 and the distance (L1 + L2) between the heat exchanger 3 and the second end portion 22b are both minimal at the circumferential position C1. .
  • the increase rate of the second distance L2 per angle in the rotation direction of the centrifugal fan 1 from the circumferential position C1 is an increase in the second distance L2 per angle in the counter-rotation direction of the centrifugal fan 1 from the circumferential position C1. Equal to the rate. Thereby, the increase rate of the distance per angle (L1 + L2) in the rotation direction of the centrifugal fan 1 from the circumferential position C1 is the distance per angle (L1 + L2) in the counter-rotation direction of the centrifugal fan 1 from the circumferential position C1. It is smaller than the rate of increase.
  • an area where the distance (L1 + L2) increases in the rotation direction of the centrifugal fan 1 in the space sandwiched between the second partition wall 22 and the heat exchanger 3 is defined as an enlarged air passage 32.
  • a region where the distance (L1 + L2) decreases in the rotation direction of the centrifugal fan 1 in the space between the second partition wall 22 and the heat exchanger 3 is defined as a reduced air path 33.
  • the enlarged air passage 32 and the reduced air passage 33 are adjacent to each other in the circumferential direction across the circumferential position C1.
  • the enlarged air passage 32 is located on the rotational direction side of the circumferential position C1, and the reduced air passage 33 is located on the counter-rotating direction side of the circumferential position C1.
  • the second partition 22 serves as an air passage wall on the inner peripheral side of both the enlarged air passage 32 and the reduced air passage 33.
  • the enlarged air passage 32 is liable to cause separation of the air flow from the air passage wall (for example, the second partition wall 22) due to the expansion of the air passage, so that a secondary vortex is likely to occur.
  • the increasing rate of the distance (L 1 + L 2) in the rotation direction of the centrifugal fan 1 in the expansion air passage 32 is the anti-rotation direction of the centrifugal fan 1 in the reduction air passage 33. Is smaller than the increase rate of the distance (L1 + L2).
  • the expansion rate of the air path in the expansion air path 32 can be reduced. Thereby, since separation of the airflow in the enlarged air passage 32 can be suppressed, generation of secondary vortices in the enlarged air passage 32 can be suppressed. Therefore, according to this Embodiment, the increase in the pressure loss of the heat exchanger resulting from a secondary vortex can be suppressed.
  • the increasing rate of the first distance L1 in the rotational direction of the centrifugal fan 1 from the circumferential position C1 at which the first distance L1 is minimized is It is smaller than the increasing rate of the first distance L1 in the counter-rotating direction of the centrifugal fan 1 from the circumferential position C1 where the distance L1 of 1 is minimized.
  • FIG. 11 is a refrigerant circuit diagram showing the configuration of the refrigerant circuit of the air conditioner according to the present embodiment.
  • the air conditioner includes an outdoor unit 300, an indoor unit 301, and refrigerant pipes 302 and 303 that connect the outdoor unit 300 and the indoor unit 301.
  • the refrigerant channel in the outdoor unit 300 and the refrigerant channel in the indoor unit 301 are connected via the refrigerant pipes 302 and 303, thereby forming a refrigerant circuit in which the refrigerant circulates.
  • the refrigerant pipe 302 is a gas pipe through which a gas refrigerant flows
  • the refrigerant pipe 303 is a liquid pipe through which a liquid refrigerant or a gas-liquid two-phase refrigerant flows.
  • the compressor 101 is a fluid machine that compresses and discharges sucked refrigerant.
  • the compressor 101 may include an inverter device or the like.
  • the inverter apparatus can change the capacity
  • the four-way valve 102 is a flow path switching device that switches a refrigerant flow direction between a cooling operation and a heating operation based on an instruction from a control device (not shown).
  • the outdoor heat exchanger 103 heat exchange between the refrigerant and the outdoor air supplied by the outdoor blower 104 is performed.
  • the outdoor heat exchanger 103 functions as a condenser during the cooling operation. That is, in the outdoor heat exchanger 103 during the cooling operation, the high-pressure refrigerant compressed by the compressor 101 and flowing through the four-way valve 102 is condensed and liquefied by heat exchange with the outdoor air. The liquid refrigerant liquefied by the outdoor heat exchanger 103 is supplied to the expansion device 105.
  • the outdoor heat exchanger 103 functions as an evaporator during heating operation.
  • the low-pressure refrigerant decompressed by the expansion device 105 is evaporated and vaporized by heat exchange with the outdoor air.
  • the gas refrigerant evaporated in the outdoor heat exchanger 103 is sucked into the compressor 101.
  • the expansion device 105 an expansion valve whose opening degree can be adjusted is used.
  • the indoor unit 301 accommodates an indoor heat exchanger 106 and an indoor fan 107.
  • the indoor unit 100 according to any of Embodiments 1 to 3 can be used. That is, the heat exchanger 3 can be used as the indoor heat exchanger 106, and the centrifugal fan 1 can be used as the indoor fan 107.
  • the indoor heat exchanger 106 heat exchange is performed between the refrigerant and the indoor air supplied by the indoor fan 107.
  • the indoor heat exchanger 106 functions as an evaporator during the cooling operation. That is, in the indoor heat exchanger 106 during the cooling operation, the low-pressure refrigerant decompressed by the expansion device 105 and introduced through the refrigerant pipe 303 is evaporated and vaporized by heat exchange with room air. The gas refrigerant vaporized by the indoor heat exchanger 106 is sucked into the compressor 101 via the refrigerant pipe 302 and the four-way valve 102. The indoor air that has passed through the indoor heat exchanger 106 is cooled by the endothermic action of the refrigerant.
  • the indoor heat exchanger 106 functions as a condenser during heating operation. That is, in the indoor heat exchanger 106 during the heating operation, the high-pressure refrigerant compressed by the compressor 101 and flowing through the four-way valve 102 and the refrigerant pipe 302 is condensed and liquefied by heat exchange with room air. The liquid refrigerant liquefied by the indoor heat exchanger 106 is supplied to the expansion device 105 via the refrigerant pipe 303. The indoor air that has passed through the indoor heat exchanger 106 is heated by the heat dissipation action of the refrigerant.
  • the indoor fan 107 operates at a predetermined operating frequency based on, for example, user settings.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
  • Air-Flow Control Members (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'objectif de la présente invention est de fournir un climatiseur grâce auquel l'efficacité de soufflage d'un ventilateur centrifuge peut être améliorée. Ce climatiseur est pourvu : d'un ventilateur centrifuge ; d'un échangeur de chaleur disposé de façon à entourer la circonférence externe du ventilateur centrifuge ; d'une première paroi de séparation qui sépare une région côté aspiration et une région côté soufflage du ventilateur centrifuge ; et une seconde paroi de séparation qui s'étend de la première paroi de séparation vers le ventilateur centrifuge, la seconde paroi de séparation ayant une seconde partie d'extrémité qui est la partie d'extrémité sur le côté du ventilateur centrifuge. En supposant qu'une première distance est la distance dans la direction radiale entre le bord circonférentiel externe du ventilateur centrifuge et la seconde partie d'extrémité, qu'une seconde distance est la distance entre le bord circonférentiel externe et l'échangeur de chaleur, qu'une première section transversale radiale est la section transversale radiale qui passe à travers un arbre rotatif et est parallèle à l'arbre rotatif, et qu'une seconde section transversale radiale est la section transversale radiale dans laquelle la seconde distance est plus longue que la seconde distance dans la première section transversale radiale, la première distance dans la seconde section transversale radiale est plus longue que la première distance dans la première section transversale radiale.
PCT/JP2018/015086 2018-04-10 2018-04-10 Climatiseur Ceased WO2019198150A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/JP2018/015086 WO2019198150A1 (fr) 2018-04-10 2018-04-10 Climatiseur
JP2020512973A JP7055197B2 (ja) 2018-04-10 2018-04-10 空気調和機

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2018/015086 WO2019198150A1 (fr) 2018-04-10 2018-04-10 Climatiseur

Publications (1)

Publication Number Publication Date
WO2019198150A1 true WO2019198150A1 (fr) 2019-10-17

Family

ID=68162838

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2018/015086 Ceased WO2019198150A1 (fr) 2018-04-10 2018-04-10 Climatiseur

Country Status (2)

Country Link
JP (1) JP7055197B2 (fr)
WO (1) WO2019198150A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003083599A (ja) * 2001-09-11 2003-03-19 Daikin Ind Ltd 空気調和機
JP2016011827A (ja) * 2014-06-05 2016-01-21 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． 天井埋込型室内機及びそれを用いた空気調和機
WO2017006467A1 (fr) * 2015-07-08 2017-01-12 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー （ホンコン） リミテッド Unité intérieure pour climatiseur

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003083599A (ja) * 2001-09-11 2003-03-19 Daikin Ind Ltd 空気調和機
JP2016011827A (ja) * 2014-06-05 2016-01-21 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． 天井埋込型室内機及びそれを用いた空気調和機
WO2017006467A1 (fr) * 2015-07-08 2017-01-12 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー （ホンコン） リミテッド Unité intérieure pour climatiseur

Also Published As

Publication number Publication date
JPWO2019198150A1 (ja) 2021-01-14
JP7055197B2 (ja) 2022-04-15

Similar Documents

Publication Publication Date Title
CN109891155B (zh) 室内机及空调装置
WO2019082392A1 (fr) Soufflante centrifuge, dispositif de soufflante d'air, dispositif de climatisation, et dispositif à cycle de réfrigération
US20180209440A1 (en) Centrifugal blower, air conditioning apparatus, and refrigerating cycle apparatus
JP6671469B2 (ja) 遠心送風機、空気調和装置および冷凍サイクル装置
CN104713166B (zh) 室内机以及空调装置
CN110325745B (zh) 螺旋桨式风扇、送风机以及空调机
JP5295321B2 (ja) 送風機、室外機及び冷凍サイクル装置
US12038017B2 (en) Centrifugal air-sending device, air-sending apparatus, air-conditioning apparatus, and refrigeration cycle apparatus
JP6625305B1 (ja) 送風機、空気調和装置の室内機および空気調和装置
JP7130061B2 (ja) 遠心送風機、送風装置、空気調和装置及び冷凍サイクル装置
WO2016170652A1 (fr) Unité intérieure et dispositif de climatisation
WO2017060973A1 (fr) Dispositif de ventilation, unité d'extérieur, et dispositif de cycle frigorifique
JP2017048954A (ja) 空気調和機の室内機
JP7055197B2 (ja) 空気調和機
JP6925571B1 (ja) 送風機、室内機および空気調和装置
JP6430032B2 (ja) 遠心ファン、空気調和装置および冷凍サイクル装置
JP7378574B2 (ja) 室内機および空気調和装置
JP7386885B2 (ja) 室内機およびそれを備えた空気調和装置
JP7378505B2 (ja) 遠心送風機及びそれを備えた空気調和機
TWI754505B (zh) 遠心送風機的渦形殼體、具備這個渦形殼體的遠心送風機、空氣調和裝置以及冷凍循環裝置
JP7097973B2 (ja) 室内機及び冷凍サイクル装置
HK40069680A (en) Centrifugal blower, blowing device, air conditioner, and refrigeration cycle device
WO2024189871A1 (fr) Unité intérieure pour climatiseur et climatiseur équipé de celle-ci
WO2023152802A1 (fr) Unité intérieure et dispositif de climatisation la comprenant
WO2023223383A1 (fr) Ventilateur à flux transversal, dispositif de soufflage, et dispositif à cycle de réfrigération

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18914468

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2020512973

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18914468

Country of ref document: EP

Kind code of ref document: A1