WO2022002253A1 - 冷凝器组件和便携式空调器 - Google Patents

冷凝器组件和便携式空调器 Download PDF

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Publication number
WO2022002253A1
WO2022002253A1 PCT/CN2021/104264 CN2021104264W WO2022002253A1 WO 2022002253 A1 WO2022002253 A1 WO 2022002253A1 CN 2021104264 W CN2021104264 W CN 2021104264W WO 2022002253 A1 WO2022002253 A1 WO 2022002253A1
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WO
WIPO (PCT)
Prior art keywords
air
heat exchanger
section
air outlet
air inlet
Prior art date
Application number
PCT/CN2021/104264
Other languages
English (en)
French (fr)
Inventor
麻泽磊
蒋大永
王进
傅辉
Original Assignee
深圳市刻酷科技有限公司
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Filing date
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Application filed by 深圳市刻酷科技有限公司 filed Critical 深圳市刻酷科技有限公司
Publication of WO2022002253A1 publication Critical patent/WO2022002253A1/zh

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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
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/032—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by heat exchangers
    • F24F1/0323—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by heat exchangers by the mounting or arrangement of the heat exchangers
    • 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
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/022—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing comprising a compressor cycle
    • 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
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/04—Arrangements for portability
    • 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
    • F24F13/22—Means for preventing condensation or evacuating condensate
    • 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
    • F24F13/22—Means for preventing condensation or evacuating condensate
    • F24F13/222—Means for preventing condensation or evacuating condensate for evacuating condensate
    • 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
    • F24F13/24—Means for preventing or suppressing noise
    • 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
    • F24F13/24—Means for preventing or suppressing noise
    • F24F2013/247—Active noise-suppression

Definitions

  • the present application relates to the technical field of air conditioners, and in particular, to a condenser assembly and a portable air conditioner.
  • the small volume of the condensing heat exchanger leads to a small heat exchange area, which makes it difficult to increase the heat exchange of the condensing heat exchanger, and the condensing heat exchanger is arranged in parallel with the exhaust fan.
  • the method leads to a large air intake noise, which affects the cooling effect of the entire air conditioner and is difficult to meet the actual demand.
  • One of the objectives of the embodiments of the present application is to provide a condenser assembly and a portable air conditioner.
  • a condenser assembly including an exhaust fan, an air inlet section and an air outlet section, wherein the air inlet section is provided with a condensing heat exchanger, and the air outlet section is provided with the an exhaust fan, the exhaust air direction of the air inlet section is opposite to the air intake direction of the air outlet section, and the air inlet section and the air outlet section are arranged on both sides of the partition plate at intervals;
  • the included angle between the condensing heat exchanger and the air inlet direction is set at 15° to 45° to form a wedge-shaped air inlet cavity.
  • a flared section is arranged between the air inlet cavity and the air inlet of the air inlet section; an inverted wedge-shaped static pressure cavity is formed between the condensing heat exchanger and the exhaust fan , the fin combing air of the condensing heat exchanger enters the static pressure chamber from the air inlet section, and the static pressure chamber is connected to the blowing area of the exhaust fan through the exhaust port on the partition plate .
  • the exhaust port is a circular hole for exhausting air, and a tapered first air guide ring extends toward the direction of the exhaust fan from the circular hole.
  • the first air guide ring A cylindrical discharge port is formed.
  • the exhaust fan extends correspondingly toward the circular hole with a tapered second air guide ring
  • the second air guide ring is sleeved on the periphery of the first air guide ring, and is connected with the first air guide ring.
  • the first air guide ring forms an annular first gap
  • the free end of the second air guide ring forms a second gap with the corresponding position of the partition plate.
  • the first gap ranges from 1.0mm to 3.0mm.
  • the second gap ranges from 1.0mm to 3.0mm.
  • it further includes a casing forming an air duct, the casing has a bottom surface of a flat part, and the partition plate is arranged in the middle of the casing, so as to divide the cavity in the casing into air inlet sections and outlet section.
  • the exhaust fan is a centrifugal fan
  • the centrifugal fan has an airflow discharge area and an airflow rotation area between the centrifugal fan and the inner wall of the casing, and the airflow rotation area is connected to the airflow discharge area.
  • the airflow in the area has opposite components.
  • the air outlet section of the casing is arranged symmetrically in the up-down direction, the fan axis of the exhaust fan is close to or located at the symmetry line of the air outlet section, and the exhaust fan is arranged away from the air outlet.
  • the upper and lower walls of the air outlet section are gradually reduced from the position corresponding to the axis of the fan toward the condensation air outlet to the size of the condensation air outlet.
  • the chamber height at the condensation air outlet is 1/2 to 4/5 of the chamber height at the axis of the fan; one end of the air outlet section is closed, and the other end is provided with the condensation air outlet.
  • a portable air conditioner comprising a base plate and a casing connected to the base plate, an evaporative air outlet obliquely upward and an evaporative air inlet close to the evaporative air outlet are provided on the front side of the casing, and the casing
  • the rear part is provided with the condenser assembly, the shell and the bottom plate are long strips, and the evaporative heat exchanger, the compressor and the condensing heat exchanger are arranged from front to back, the evaporative heat exchanger, The compressor and the condensing heat exchanger are connected by a refrigerant pipeline.
  • a water receiving tray is further provided on the bottom plate, there is a gap between the water receiving tray and the bottom plate, and the water receiving tray includes a first water receiving tray arranged on the evaporative heat exchanger.
  • the bottom plate is further provided with a water collection cavity below the condensing heat exchanger, the water collection cavity is formed by surrounding vertical walls, and one side of the water collection cavity is connected to all the surrounding vertical walls.
  • the second water receiving section is connected to collect the condensed water flowing out from the second water receiving section; the water collecting cavity is located at the rear end of the bottom plate and is also provided with a drainage hole; or the water collecting cavity is also provided with The water wheel is used to beat the condensed water to the surface of the fins of the condensing heat exchanger.
  • the condenser assembly includes an exhaust fan, an air inlet section and an air outlet section, the air inlet section is provided with a condensing heat exchanger, and the air outlet section is provided with an exhaust fan , the exhaust air direction of the air inlet section is opposite to that of the air outlet section, and the air inlet section and the air outlet section are arranged at intervals on both sides of the partition; the angle between the condensing heat exchanger and the air inlet direction is 15° to 45° setting to form a wedge-shaped air inlet cavity.
  • the portable air conditioner includes a base plate and a casing connected to the base plate, and an evaporative air outlet obliquely upward and an evaporative air outlet close to the evaporative air outlet are arranged on the front side of the casing.
  • the evaporative air inlet is provided with the above-mentioned condenser assembly at the rear of the casing.
  • the casing and the bottom plate are arranged in a strip shape, and an evaporative heat exchanger, a compressor and a condensing heat exchanger are arranged from the front to the back.
  • the evaporative heat exchange The compressor, the compressor and the condensing heat exchanger are connected by a refrigerant pipeline.
  • FIG. 1 is a schematic structural diagram of a portable air conditioner according to an embodiment of the application.
  • FIG. 2 is a schematic structural diagram of the portable air conditioner according to the embodiment of the application in the front view direction;
  • Fig. 3 is the sectional view of A-A in Fig. 2;
  • Fig. 4 is an enlarged view of part A in Fig. 5;
  • FIG. 5 is a cross-sectional view of a condenser assembly according to an embodiment of the application.
  • FIG. 6 is a schematic structural diagram of a portable air conditioner according to an embodiment of the present application in a top view direction;
  • Fig. 7 is the sectional view of B-B in Fig. 6;
  • FIG. 8 is a schematic partial structure diagram of a portable air conditioner according to an embodiment of the application.
  • FIG. 9 is a partial structural schematic diagram of the portable air conditioner according to the embodiment of the application in another view direction.
  • FIG. 10 is a schematic structural diagram of an evaporative heat exchanger, a water receiving tray and a bottom plate of a portable air conditioner according to an embodiment of the present application.
  • Handle piece 101 evaporative air outlet 102, evaporative air inlet 103, condensation air outlet 104, condensation air inlet 105, condensing heat exchanger 106, compressor 107, air inlet fan 108, evaporative heat exchanger 109, exhaust fan 117 , bottom plate 142, electric control box 161, water receiving tray 162, first water receiving section 1621, second water receiving section 1622, capillary tube 163, refrigerant pipe connecting section 164, fixing block 165, water retaining rib 166, drainage hole 167, Water collecting cavity 168, fixing ears 171, baffle 180, air inlet cavity 181, static pressure cavity 182, exhaust port 183, first air guide ring 184, first inner air guide surface 184a, first outer air guide surface 184b , the second wind guide ring 185, the second inner wind guide surface 185a, the first shell 186, the second shell 187, the air inlet section 188, the air outlet section 189, the flared section 190, and the shell 199.
  • Some embodiments of the present application disclose a condenser assembly, as shown in FIGS. 2 to 9 , including an exhaust fan 117 , an air inlet section 188 and an air outlet section 189 , and the air inlet section 188 is provided with a condensing heat exchanger 106 , the air outlet section 189 is provided with an exhaust fan 117, the exhaust wind direction of the air inlet section 188 is opposite to the air inlet wind direction of the air outlet section 189, and the air inlet section 188 and the air outlet section 189 are arranged on both sides of the partition plate 180 at intervals.
  • the angle between the condensing heat exchanger 106 and the air inlet direction is set at 15° to 45° to form a wedge-shaped air inlet cavity 181 .
  • the air inlet section 188 is provided with a condensation air inlet 105
  • the air outlet section 189 is provided with a condensation air outlet 104.
  • the air inlet section 188 and the air outlet section 189 are isolated by the partition plate 180.
  • the air section 188 enters the air outlet section 189 through the condensing heat exchanger 106 for heat exchange, and is discharged from the air outlet section 189 through the condensation air outlet 104 through the high-speed rotation of the exhaust fan 117 to form an air duct for airflow.
  • the air inlet section 188 and the air outlet section 189 are separated by the partition plate 180, so that the chamber of the air inlet section 188 and the chamber of the air outlet section 189 are arranged side by side, and the condensation air inlet 105 and the condensation air outlet 104 are also arranged side by side. It is beneficial to the compact structure of the entire air inlet section 188 and the air outlet section 189. As shown in FIG.
  • the condensing heat exchanger 106 is inclined in the chamber of the air inlet section 188 . Specifically, the condensing heat exchanger 106 moves from the side of the condensing air inlet 105 close to the partition plate 180 to the distance away from the inner side of the air inlet section 188 . One end of the plate 180 is inclined and arranged, and the surface of the condensing heat exchanger 106 forms an angle ⁇ 1 with the air inlet direction as shown in FIG. 5 to form a wedge-shaped air inlet cavity 181.
  • the contact area between the airflow entering from the condensing air inlet 105 and the condensing heat exchanger 106 is increased, so that the surface of the air inlet of the entire condensing heat exchanger 106 will have a relatively uniform airflow entering, thereby
  • the airflow on the outlet side of the condensing heat exchanger 106 is also more uniform, so that the airflow entering the exhaust fan 117 is also more uniform, and finally the airflow discharged from the condensation exhaust port 104 is uniform.
  • the air flow entering from the condensing air inlet 105 is unevenly distributed on the air inlet surface of the condensing heat exchanger 106, The closer to the surface of the condensing air inlet 105, as shown in the air1 part of air flow in Fig.
  • the air flow can form a uniform air inlet surface in the condensing heat exchanger 106 , thereby making the air flow through the condensing heat exchanger 106 uniform.
  • the included angle ⁇ 1 may be 20° to 35°, and ⁇ 1 in FIG. 5 is about 22°.
  • a flared section 190 is provided between the air inlet cavity 181 and the air inlet of the air inlet section 188 , as shown in FIG.
  • the air inlet cavity 181 has a flared section 190 whose diameter is tapered from the air inlet direction, so that the air flow is compressed after passing through this section, thereby increasing the air pressure entering the air inlet cavity 181, which helps to improve the air flow through the air inlet cavity 181.
  • the speed of the airflow of the condensing heat exchanger 106 further enhances the heat exchange efficiency of the condensing heat exchanger 106 .
  • an inverted wedge-shaped static pressure cavity 182 is formed between the condensing heat exchanger 106 and the exhaust fan 117 , and the fin combing air of the condensing heat exchanger 106 enters the static pressure cavity from the air inlet section 188 182 , the static pressure chamber 182 is connected to the blowing area of the exhaust fan 117 through the exhaust port 183 on the partition plate 180 .
  • the shape of the static pressure chamber 182 is substantially the same as the shape of the air inlet chamber 181 , and they are oppositely arranged.
  • the space of the air duct after the airflow is output from the condensing heat exchanger 106 is increased, so that the flow velocity of the airflow here is reduced, thereby increasing the static pressure, and making use of the airflow more smoothly.
  • the pressure chamber 182 enters the exhaust fan 117 through the exhaust port 183, and the pressure of the static pressure chamber 182 is relatively uniform, so that the air flow rate passing through the condensing heat exchanger 106 is uniform, which can further improve its heat exchange efficiency and reduce the air flow at the same time. Pass the noise of the condensing heat exchanger 106 and the exhaust port 183 .
  • the exhaust port 183 is a circular hole for exhausting air, and a tapered first air guide extends toward the direction of the exhaust fan 117 from the circular hole.
  • a ring 184, the first air guide ring 184 forms a cylindrical discharge port.
  • the exhaust port 183 is a circular circular hole, and the circular hole is provided with a first air guide ring 184 whose diameter is tapered toward the direction of the exhaust fan 117 , and the first air guide ring 184 has an arc-shaped first inner guide ring 184 .
  • the wind surface 184a, the first wind guide surface 184a extends toward the axial direction of the exhaust fan 117, so that when the airflow passes through the circular hole in the static pressure chamber 182, it is guided by the first inner wind guide surface 184a, forming
  • the airflow consistent with the axial direction of the exhaust fan 117 is the airflow air3 in FIG. 4 , so as to further reduce the noise generated when the airflow passes through the exhaust port 183 .
  • the exhaust fan 117 extends a tapered second air guide ring 185 toward the circular hole correspondingly, and the second air guide ring 185 is sleeved on the first air guide ring 185 .
  • the periphery of an air guide ring 184 forms an annular first gap with the first air guide ring 184, and a second gap is formed between the free end of the second air guide ring 185 and the corresponding position of the partition plate 180, and the range of the first gap is 1.0 mm to 3.0mm with a second gap ranging from 1.0mm to 3.0mm.
  • the exhaust fan 117 is also provided with a second air guide ring 185 opposite to the first air guide ring 184.
  • the aperture of the second air guide ring 185 is larger than that of the first air guide ring 184, so that it is sleeved on the first air guide ring 184.
  • the first wind guide ring 184 and the second wind guide ring 185 have overlapping areas in the wind inlet direction, that is, there are a first outer wind guide surface 184b and a second wind guide surface formed by the outer surface of the first wind guide ring 184
  • the axes of the fans 117 are the same.
  • the second air guide ring 185 Since the second air guide ring 185 is connected to the wind wheel of the exhaust fan 117, the second air guide ring 185 and the exhaust fan 117 rotate synchronously during operation, so a certain gap needs to be reserved between the circular hole and the wind wheel to prevent Avoid interference affecting the rotation of the wind wheel.
  • the high-speed airflow formed by the exhaust fan 117 has wind pressure around the wind wheel of the exhaust fan 117, and there is a certain negative pressure inside the wind wheel, thus causing a part of the air flow It is sucked through the gap and then enters the inside of the wind wheel.
  • the part of the air flow will enter the inside of the wind wheel along the wall surface of the partition plate 180,
  • the air flow direction is consistent with the surface of the partition plate 180, and this part of the air flow direction is roughly perpendicular to the air flow direction entering from the circular hole along the axis of the exhaust fan 117, so the two form conflicting interference at the gap, thereby forming a relatively
  • the loud abnormal sound is like a whistling sound, which will interfere with the user's use.
  • a first air guide ring 184 is provided at the circular hole, and a second air guide ring 185 is provided at one end of the wind wheel of the exhaust fan 117, so as to form an axis with the fan between the two air guide rings.
  • the air guide channel with the same direction, as shown in FIG. 4 when a part of the air flow is the air flow air4 in FIG.
  • the direction of the airflow air3 is the same, that is, the direction of the axis of the exhaust fan 117 is the same, so that the two will not cause interference, thereby eliminating the above-mentioned abnormal sound caused by the interference, thereby improving the user experience when using.
  • the above-mentioned first gap and second gap are selected to a suitable gap range value mentioned above, which can not only satisfy the situation that the round hole does not interfere with the long-term operation of the wind rotor, but also form a suitable wind guide. channel to avoid the formation of abnormal airflow.
  • the value is 1.5 mm to 2.0 mm, such as 1.7 mm.
  • the condenser assembly further includes a casing forming an air duct, the casing has a bottom surface of a flat part, and a partition 180 is disposed in the middle of the casing to divide the cavity in the casing into air intake sections 188 and outlet section 189.
  • the outer shell covers the surface of the condenser assembly and has a flat bottom surface, which is convenient for installing the condensing heat exchanger 106 and the exhaust fan 117 , and the partition 180 divides the cavity in the outer shell into two parts. That is, the air inlet section 188 and the air outlet section 189 are juxtaposed.
  • the casing specifically includes a first casing 186 covering the side of the condensing heat exchanger 106 as shown in FIG. 8 , and a second casing 187 covering the side of the exhaust fan 117 as shown in FIG. 9 .
  • the exhaust fan 117 is a centrifugal fan.
  • the centrifugal fan has an airflow discharge area and an airflow rotation area between the centrifugal fan and the inner wall of the housing.
  • the airflow in the airflow rotation area and the airflow discharge area have opposite components. As shown in FIG. 7 , when the centrifugal fan rotates at high speed, the air flow sucked by the blades of the wind rotor from the circular hole along the axial direction of the fan is continuously discharged to the area between the wind rotor and the condensation exhaust port 104 along the rotation direction of the wind rotor.
  • the area between the two most of the airflow is delivered to the outside of the condensation exhaust port 104 as the airflow air5 in Figure 7, so the area is the airflow discharge area, because of the lack of the volute structure, a small part of the airflow will continue along the
  • the wind rotor is rotated to the area between the wind rotor and the inner wall of the second housing 187, such as the airflow air6 in Figure 7, this area is the airflow rotation area, and the airflow in the airflow rotation area and the airflow in the airflow discharge area contain opposite directions.
  • the air outlet section 189 of the casing that is, the cavity where the second casing 187 is located is symmetrically arranged in the up-down direction, and the fan axis of the exhaust fan 117 is close to or located at the air outlet section 189 .
  • the symmetry line of the air outlet section 189 is L1 in FIG. 7 . Specifically, as shown in FIG. 7 and FIG.
  • the air outlet section 189 of the outer casing that is, the second outer casing 187 includes two parts, and the front end is an arc-shaped semicircle, such as In the cross-sectional view shown in FIG. 7 , the position starting from the boundary line L2 that passes through the axis C1 of the exhaust fan 117 and is perpendicular to the symmetry line L1 is the rear end, and the rear end starts from the boundary line L2 to the condensation exhaust port.
  • the arc section at the front end is adapted to the shape of the exhaust fan 117, and the tapered section at the rear end makes the airflow in the airflow discharge area gradually compressed to increase
  • the air flow rate discharged from the condensing air outlet 104 is discharged farther back, because the condensing air inlet 105 and the condensing air outlet 104 are arranged side by side at the rear end of the casing, and the two are relatively close, and the condensing air outlet 104
  • the discharged air with a higher velocity helps to reduce the chance of directly entering the condensing air inlet 105 , and reduces the airflow interference between the two to improve the heat exchange capacity of the condensing heat exchanger 106 .
  • the height of the second housing 187 at the condensation exhaust port 104 is H1 , which is at the dividing line L2
  • the height of the position corresponding to the axis of the exhaust fan 117 is H2, wherein the ratio of H1 to H2 ranges from 1/2 to 4/5, that is, the range of 0.5 to 0.8.
  • the value of this range can be further taken as 0.55 to 0.75, as shown in the figure
  • the scale value in 7 is 0.61.
  • the present application also proposes a portable air conditioner, as shown in FIG. 1 to FIG. 10 , comprising a bottom plate 142 and a casing 199 connected to the bottom plate 142 , and an evaporative air outlet 102 obliquely upward is provided on the front side of the casing 199 and a
  • the evaporative air inlet 103 close to the evaporative air outlet 102 is provided with the above-mentioned condenser assembly at the rear of the casing 199.
  • the casing 199 and the bottom plate 142 are arranged in long strips, and the evaporative heat exchanger 109, compression
  • the compressor 107 and the condensing heat exchanger 106, the evaporative heat exchanger 109, the compressor 107 and the condensing heat exchanger 106 are connected by refrigerant pipes to form a refrigeration system.
  • the evaporative air inlet 103 , the evaporative heat exchanger 109 and the wind rotors of the air inlet fan 108 are arranged substantially vertically and in parallel, and the evaporative air outlet 102 is inclined upward, which is located at the air inlet fan.
  • the refrigeration cycle components including the evaporative heat exchanger 109 and the heating cycle components including the condensing heat exchanger 106 are respectively arranged on both sides of the compressor 107, so that the center of gravity of the entire air conditioner is evenly distributed, which is more suitable and convenient to carry.
  • a handle 101 can be provided on the upper surface of the housing of the air conditioner, so that the entire air conditioner can be easily and stably lifted for transportation by holding the handle 101 .
  • the bottom plate 142 is further provided with a water receiving tray 162 , the water receiving tray 162 has a first water receiving section 1621 disposed under the evaporative heat exchanger 109 , and the water receiving tray is 162 is inclined from the front to the rear, the water receiving tray 162 is located above the bottom plate 142 and there is a gap between the bottom plate 142 and the bottom plate 142 .
  • the water receiving tray 162 is surrounded by vertical walls to form a water-containing cavity.
  • the amount of water droplets produced by the condensation is much less than that of the condensed water. Even if it drips onto the bottom plate 142, a very small amount of water will be removed by the relatively high temperature.
  • the bottom plate 142 evaporates without substantially reducing the temperature of the bottom plate 142 .
  • the water receiving tray 162 is arranged to be inclined from the front side of the evaporative heat exchanger 109 to the rear side of the condensing heat exchanger 106, so that the condensed water dropped by the evaporative heat exchanger 109 can be quickly flowed away by the water receiving tray 162, It will not accumulate at the position of the first water receiving section 1621 to cause overflow.
  • the water receiving tray 162 further includes a second water receiving section 1622, the water receiving section is in the shape of a narrow sheet, and is arranged under the refrigerant pipeline, and the refrigerant pipeline is connected to the suction of the compressor 107
  • the pipeline from the tube to the evaporative heat exchanger 109 is specifically the refrigerant tube connection section 164 shown in FIG. 3 .
  • the gaseous refrigerant with high temperature and high pressure is in the refrigerant pipe coming out of the exhaust port of the compressor 107, and after the heat is discharged to the outside through the condensing heat exchanger 106 to cool the refrigerant in the refrigerant pipe, it becomes
  • the low-temperature and high-pressure liquid refrigerant is throttled and depressurized by the throttling and pressure-reducing components such as the capillary 163 to become the medium-temperature and high-pressure liquid refrigerant with a slightly lower temperature, and then enters the evaporative heat exchanger 109, and absorbs heat to the surrounding environment through the evaporative heat exchanger 109
  • the temperature of the refrigerant increases, and the temperature in the refrigerant pipes in the evaporative heat exchanger 109 is very low, so that the temperature of the fins of the evaporative heat exchanger 109 installed in the refrigerant pipes is also very low, so
  • the water drops to the first water receiving section 1621 of the water receiving tray 162 below the evaporative heat exchanger 109, and after exiting the evaporative heat exchanger 109, it becomes a low-temperature gaseous refrigerant, and finally enters the suction port of the compressor 107 and is then fed by The compressor 107 compresses the gaseous refrigerant into a high temperature and high pressure refrigerant, and circulates in this way.
  • the refrigerant pipe connecting the inlet and outlet of the evaporative heat exchanger 109 will also absorb heat to the outside, so that the temperature of the refrigerant pipe is very low, generally lower than 2°, so this section of the refrigerant pipe will also easily generate condensed water, especially the connection
  • the refrigerant pipe at the suction port of the compressor 107 is the refrigerant pipe connection section 164, and the refrigerant pipe connecting the evaporative heat exchanger 109 and the condensing heat exchanger 106 is mainly a capillary tube 163, and its diameter is relative to the refrigerant pipes in other positions. It is much smaller, so it produces much less condensate and is less prone to dripping.
  • the refrigerant pipe connecting the suction port of the compressor 107 is preferably arranged above the water receiving tray 162, that is, above the second water receiving section 1622, so as to receive dripping condensed water.
  • the capillary 163 that connects the refrigerant pipe section between the evaporating heat exchanger 109 and the condensing heat exchanger 106 is also disposed above the second water receiving section 1622, so as to reduce the condensation generated therefrom. The phenomenon in which water droplets fall on the drip tray 162 .
  • several fixing blocks 165 are provided on the bottom plate 142 , and the water receiving tray 162 is installed on these fixing blocks 165 .
  • the structure, such as a fixing column, is convenient for fixing the water receiving tray 162 on the fixing block 165 by fixing components such as screws.
  • the second water receiving section 1622 has a surrounding frame forming a tail opening.
  • the surrounding frame includes vertical ribs and horizontal ribs extending horizontally along both sides of the bottom plate 142 .
  • the first water-receiving section 1621 forms a water-receiving cavity with vertical walls around it, and the water-receiving section is arranged in a strip shape in the left-right direction to fit with the bottom surface of the evaporative heat exchanger 109, and the second water-receiving section connected with it
  • the water receiving section 1622 is arranged in the shape of a long strip in the front and rear directions, and vertical walls formed by vertical ribs are provided on both sides of the water receiving section 1622.
  • the horizontal ribs are integrally connected to form a surrounding frame.
  • the direction of the second water receiving section 1622 is approximately at right angles to the first water receiving section 1621.
  • the rear end of the vertical ribs is provided with a connection structure with the rear of the bottom plate 142.
  • the fixing ears 171 are arranged close to the horizontal bars and on the two sides of the vertical bars.
  • the middle of the fixing ears 171 is provided with screw holes, and the bottom plate 142 is provided with fixing posts at corresponding positions to fix the fixing ears 171 on the fixing posts by screws. Therefore, the second water receiving section 1622 is fixed on the bottom plate 142 .
  • a water collecting cavity 168 surrounded by vertical walls.
  • One side of the water collecting cavity 168 is connected to the second water receiving section 1622 to collect water
  • the water collecting cavity 168 is arranged below the condensing heat exchanger 106, and its purpose is to use the air conditioner to operate at a higher temperature of the condensing heat exchanger 106 than the ambient temperature, and the water collecting cavity 168
  • the water in the water tank plays a certain role of evaporation to reduce its water level, and a drainage hole 167 is also provided in the water collecting cavity 168 at the rear end of the bottom plate 142.
  • the drainage hole 167 is blocked by a rubber plug during normal operation.
  • the rubber plug is pulled out to drain the water in the water collection chamber 168, or a drain pipe (not shown in the figure) can be further connected to the drain hole 167 to drain the water in the water collection chamber 168.
  • a drain pipe (not shown in the figure) can be further connected to the drain hole 167 to drain the water in the water collection chamber 168.
  • the other end of the drain pipe can be placed in a large tub, so as to continuously receive the condensed water in the water collecting chamber 168 .
  • a handle member 101 is provided on the housing 199 , and a water retaining rib 166 is provided on the bottom plate 142 on the other side of the water collecting cavity 168 to form a water blocking area.
  • An electric control box 161 is installed at the location of the water-proof area, and the handle member 101 is arranged above the housing 199, so that the air conditioner can be carried by holding the handle member 101.
  • the compressor 107 is installed near the center of the bottom plate 142, and the electric control box 161 and the second water receiving section 1622 are respectively disposed on both sides of the compressor 107.
  • the electric control box Water accumulates on the bottom plate 142 below 161, so that when the accumulated water is high, it enters the inside of the electric control box 161, causing the circuit board inside the electric control box 161 to short-circuit and cause the air conditioner to fail.
  • the area of the bottom plate 142 under the electric control box 161 should be kept as dry as possible. Therefore, the water retaining ribs 166 are further arranged in the area where the exhaust fan 117 is installed, so as to prevent the water overflowing from the water collecting cavity 168 from spreading to the area below the electric control box 161, thereby ensuring the safety of the electric control board inside the electric control box 161. sex.
  • first and second are only used for descriptive purposes, and should not be construed as indicating or implying relative importance or implying the number of indicated technical features. Thus, a feature delimited with “first”, “second” may expressly or implicitly include at least one of that feature.
  • plurality means at least two, such as two, three, etc., unless expressly and specifically defined otherwise.
  • the terms “installed”, “connected”, “connected”, “fixed” and other terms should be understood in a broad sense, for example, it may be a fixed connection or a detachable connection , or integrated; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between the two elements, unless otherwise specified limit.
  • installed may be a fixed connection or a detachable connection , or integrated; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between the two elements, unless otherwise specified limit.
  • a first feature "on” or “under” a second feature may be in direct contact with the first and second features, or the first and second features indirectly through an intermediary get in touch with.
  • the first feature being “above”, “over” and “above” the second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is level higher than the second feature.
  • the first feature being “below”, “below” and “below” the second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature has a lower level than the second feature.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)

Abstract

一种冷凝器组件和便携式空调器，该冷凝器组件包括排风风机(117)、进风段(188)和出风段(189)，进风段(188)设置有冷凝换热器(106)，出风段(189)设置有排风风机(117)，进风段(188)的风向与出风段(189)的风向相反，且进风段(188)与出风段(189)间隔设置于隔板(180)的两侧；冷凝换热器(106)与进风方向的夹角为15°至45°设置，以形成楔形的进风腔(181)，使进风腔(181)内的气流与冷凝换热器(106)的接触面积增大，整个冷凝换热器(106)的进风表面都有较均匀的气流进入，从而使得冷凝换热器(106)的出风一侧的气流也较均匀，以此提高冷凝换热器(106)的换热效率，并降低气流噪音。

Description

冷凝器组件和便携式空调器
本申请要求于2020年07月03日在中国专利局提交的、申请号为202010629319.6、申请名称为“冷凝器组件和便携式空调器”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及空调器技术领域，具体涉及一种冷凝器组件和便携式空调器。
 背景技术
便携式空调器由于体积较小，结构紧凑，其冷凝换热器的体积较小导致换热面积小，难以提升冷凝换热器的换热量，而且冷凝换热器与排风风机平行的排布方式导致进风噪音较大，从而影响到整个空调器的制冷效果难以满足实际的需求。
 技术问题
本申请实施例的目的之一在于：提供一种冷凝器组件和便携式空调器。
 技术解决方案
本申请实施例采用的技术方案是：
第一方面，提供了一种冷凝器组件，包括排风风机、进风段和出风段，其特征在于，所述进风段设置有冷凝换热器，所述出风段设置有所述排风风机，所述进风段的排风风向与所述出风段的进风风向相反，且所述进风段与所述出风段间隔设置于隔板的两侧；
所述冷凝换热器与进风方向的夹角为15°至45°设置，以形成楔形的进风腔。
在一个实施例中，所述进风腔与所述进风段的入风口之间设置有扩口段；所述冷凝换热器与所述排风风机之间形成有倒楔形的静压腔，所述冷凝换热器的翅片梳理空气从所述进风段进入所述静压腔，所述静压腔通过所述隔板上的排气口连接至所述排风风机的吹风区域。
在一个实施例中，所述排气口为用于排气的圆孔，所述圆孔处向所述排风风机的方向延伸出渐缩的第一导风圈，该第一导风圈形成圆筒形排出口。
在一个实施例中，所述排风风机向所述圆孔方向对应延伸出渐缩的第二导风圈，该第二导风圈套设在所述第一导风圈外围，并与所述第一导风圈形成环状的第一间隙，且第二导风圈的自由端与所述隔板对应位置形成第二间隙，所述第一间隙范围为1.0mm至3.0mm，所述第二间隙范围为1.0mm至3.0mm。
在一个实施例中，还包括形成风道的外壳，所述外壳有平坦部分的底面，所述隔板设置于所述外壳的中部，以将所述外壳内所在的腔体分为进风段和出风段。
在一个实施例中，所述排风风机为离心风机，所述离心风机有气流排出区域，以及所述离心风机与所述外壳内壁面之间的气流回转区域，所述气流回转区域与气流排出区域的气流存在相反的分量。
在一个实施例中，所述外壳的出风段在上下方向对称设置，所述排风风机的风机轴线靠近或者位于所述出风段的对称线，且所述排风风机设置于远离出风段的冷凝排风口的一侧，所述出风段的上下壁面从所述风机轴线对应的位置朝向所述冷凝排风口逐渐缩小至所述冷凝排风口大小，所述出风段在所述冷凝排风口处的腔室高度为在所述风机轴线处的腔室高度的1/2至4/5；所述出风段的一端封闭，另一端设置所述冷凝排风口。
第二方面，提供了一种便携式空调器，包括底板和与底板连接的壳体，在壳体的前侧设置有斜向上的蒸发出风口以及与蒸发出风口靠近的蒸发进风口，在壳体的后部设置有所述的冷凝器组件，所述的壳体和底板为长条形设置，从前到后设置有蒸发换热器、压缩机和冷凝换热器，所述蒸发换热器、压缩机和冷凝换热器之间通过冷媒管路连接。
在一个实施例中，在所述底板上还设置有接水盘，所述接水盘与所述底板之间存在间隔，所述接水盘包括设置在所述蒸发换热器写的第一接水段和设置在冷媒管路段下的第二接水段，其中所述冷媒管路为连接压缩机吸气管至所述蒸发换热器的所述冷媒管路。
在一个实施例中，所述底板的位于冷凝换热器的下方还设置有集水腔，所述集水腔由四周的竖直壁面围合而成，所述集水腔的一侧与所述第二接水段连接，以收集从所述第二接水段流出的冷凝水；所述集水腔位于底板的后端还设置有排水孔；或在所述集水腔上还设置有打水轮，以将冷凝水打水至所述冷凝换热器的翅片的表面。
 有益效果
本申请实施例提供的一种冷凝器组件的有益效果在于：冷凝器组件包括排风风机、进风段和出风段，进风段设置有冷凝换热器，出风段设置有排风风机，进风段的排风风向与出风段的进风风向相反，且进风段与出风段间隔设置于隔板的两侧；冷凝换热器与进风方向的夹角为15°至45°设置，以形成楔形的进风腔。
本申请实施例提供的一种便携式空调器的有益效果在于：便携式空调器包括底板和与底板连接的壳体，在壳体的前侧设置有斜向上的蒸发出风口以及与蒸发出风口靠近的蒸发进风口，在壳体的后部设置有上述的冷凝器组件，的壳体和底板为长条形设置，从前到后设置有蒸发换热器、压缩机和冷凝换热器，蒸发换热器、压缩机和冷凝换热器之间通过冷媒管路连接。
 附图说明
为了更清楚地说明本申请实施例中的技术方案，下面将对实施例或示范性技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本申请的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图获得其它的附图。
图1为本申请实施例的便携式空调器的结构示意图；
图2为本申请实施例的便携式空调器的正视方向的结构示意图；
图3为图2中A-A的剖视图；
图4为图5中A部分的放大图；
图5为本申请实施例的冷凝器组件的剖视图；
图6为本申请实施例的便携式空调器的俯视方向的结构示意图；
图7为图6中B-B的剖视图；
图8为本申请实施例的便携式空调器的局部结构示意图；
图9为本申请实施例的便携式空调器的另一视图方向的局部结构示意图；
图10为本申请实施例的便携式空调器的蒸发换热器、接水盘和底板的结构示意图。
附图标记：
把手件101，蒸发出风口102，蒸发进风口103，冷凝排风口104，冷凝入风口105，冷凝换热器106，压缩机107，进风风机108，蒸发换热器109，排风风机117，底板142，电控盒161，接水盘162，第一接水段1621，第二接水段1622，毛细管163，冷媒管连接段164，固定块165，挡水筋166，排水孔167，集水腔168，固定耳171，隔板180，进风腔181，静压腔182，排气口183，第一导风圈184，第一内导风面184a，第一外导风面184b，第二导风圈185，第二内导风面185a，第一外壳186，第二外壳187，进风段188，出风段189，扩口段190，壳体199。
 本发明的实施方式
为了使本申请的目的、技术方案及优点更加清楚明白，以下结合附图及实施例，对本申请进行进一步详细说明。应当理解，此处所描述的具体实施例仅用以解释本申请，并不用于限定本申请。
为了说明本申请所提供的技术方案，以下结合具体附图及实施例进行详细说明。
本申请的一些实施例公开了一种冷凝器组件，如图2至图9所示，包括排风风机117、进风段188和出风段189，进风段188设置有冷凝换热器106，出风段189设置有排风风机117，进风段188的排风风向与出风段189的进风风向相反，且进风段188与出风段189间隔设置于隔板180的两侧，冷凝换热器106与进风方向的夹角为15°至45°设置，以形成楔形的进风腔181。如图3和图5所示，进风段188设置有冷凝入风口105，出风段189设置有冷凝排风口104，通过隔板180将进风段188和出风段189实现隔离，二者通过进入排风风机117的气流通道贯通，排风风机117工作时，使得出风段189的排风风机117内存在负压区，以此外界的空气被吸入从冷凝入风口105进入到进风段188，经过冷凝换热器106进行换热进入到出风段189，经排风风机117的高速旋转途径出风段189经冷凝排风口104排出，以此形成气流的风道。而进风段188和出风段189由隔板180隔离，使得进风段188的腔室和出风段189的腔室并列排布，其冷凝入风口105和冷凝排风口104也并列排布，有利于整个进风段188和出风段189的结构排布紧凑。如图5所示，冷凝换热器106在进风段188的腔室内倾斜设置，具体是冷凝换热器106从冷凝入风口105靠近隔板180的一侧向进风段188内侧的远离隔板180的一端倾斜设置，冷凝换热器106的表面与进风方向形成如图5的夹角φ1，以形成楔形的进风腔181，相对现有技术中冷凝换热器106与进风风向平行或者接近平行的设置方式，从冷凝入风口105进入的气流与冷凝换热器106的接触面积增大，使得整个冷凝换热器106的进风的表面都会有较均匀的气流进入，以此使得冷凝换热器106的出风的一侧的气流也较均匀，从而使得进入排风风机117的气流也是较均匀的，最终从冷凝排风口104排出的气流均匀。而在现有技术的冷凝换热器106与进风方向平行或者接近平行的设置方案中，其从冷凝入风口105进入的气流在冷凝换热器106的进风的表面是分布不均匀的，越是靠近冷凝入风口105的表面如图5中的air1部分气流其在冷凝换热器106的表面接触量越少，而越是远离冷凝入风口105的表面如图5中的air2部分气流在冷凝换热器106的表面接触量越多，以此导致通过冷凝换热器106的气流分布不均匀，影响冷凝换热器106对气流的换热效率，进而使得最终从冷凝排风口104排出的气流不均匀，而且气流在远离冷凝入风口105的进风腔181内的量较多，容易在此次沿着腔体的内壁面形成回旋效应导致扰流，进而会形成较大的气流噪音。因此会使得整个冷凝换热器106组件工作时噪音增大。通过合理的设置冷凝换热器106与进风方向的夹角可使得气流在冷凝换热器106形成均匀的入风面，进而使得通过冷凝换热器106的气流均匀。该夹角φ1可为20°至35°，如图5中的φ1约为22°。
在本申请的一些实施例中，进风腔181与进风段188的入风口之间设置有扩口段190，如图5所示，在冷凝入风口105到进入到冷凝换热器106所在的进风腔181处有一段口径从进风风向渐缩的扩口段190，以此使得气流经过此段后被压缩从而增大进入到进风腔181中的气流压力，有助于提升通过冷凝换热器106的气流流量的速度，进而增强冷凝换热器106的换热效率。
在本申请的一些实施例中，冷凝换热器106与排风风机117之间形成有倒楔形的静压腔182，冷凝换热器106的翅片梳理空气从进风段188进入静压腔182，静压腔182通过隔板180上的排气口183连接至排风风机117的吹风区域。结合图3和图5，静压腔182的形状设置与进风腔181的形状基本相同，呈相对设置。通过设置倒楔形的静压腔182，使得气流从冷凝换热器106输出后其风道的空间增加，从而使得气流在此处的流速降低，因而提升静压，有利用气流更顺畅的从静压腔182经排气口183进入到排风风机117中，而且静压腔182压力较均匀，使得经过冷凝换热器106了的气流流速均匀，能进一步提升其换热效率，并同时减少气流途径冷凝换热器106以及排气口183的噪音。
在本申请的一些实施例中，如图3和图4所示，排气口183为用于排气的圆孔，圆孔处向排风风机117的方向延伸出渐缩的第一导风圈184，该第一导风圈184形成圆筒形排出口。具体的，排气口183为圆形的圆孔，圆孔设置有朝向排风风机117方向孔径大小渐缩的第一导风圈184，第一导风圈184具有弧形的第一内导风面184a，该第一导风面184a的朝向排风风机117的轴线方向延伸，以此使得气流在静压腔182内经过圆孔时，被该第一内导风面184a进行导向，形成与排风风机117轴线方向一致的气流如图4中的气流air3，以此能进一步降低气流经过排气口183时形成的噪音。
在本申请的一些实施例中，如图3和图4所示，排风风机117向圆孔方向对应延伸出渐缩的第二导风圈185，该第二导风圈185套设在第一导风圈184外围，并与第一导风圈184形成环状的第一间隙，且第二导风圈185的自由端与隔板180对应位置形成第二间隙，第一间隙范围为1.0mm至3.0mm，第二间隙范围为1.0mm至3.0mm。其中排风风机117也设置有相对第一导风圈184的第二导风圈185，第二导风圈185的孔径大于第一导风圈184，以此套设在第一导风圈184外围，第一导风圈184和第二导风圈185在进风风向上存在重叠区域，即存在由第一导风圈184的外表面形成的第一外导风面184b和第二导风圈185的内表面形成的第二内导风面185a，其中第一外导风面184b和第二内导风面185a均为弧形，二者之间形成的导风通道方向为与排风风机117的轴线一致。由于第二导风圈185与排风风机117的风轮连接，因此第二导风圈185与排风风机117在工作时同步旋转，因而圆孔与风轮之间需要预留一定的间隙以避免干涉影响风轮的转动，在排风风机117高速旋转过程中，其形成的高速气流在排风风机117的风轮周围存在风压，而风轮内部存在一定的负压，因此导致一部分气流被吸入经该间隙再进入到风轮内部。如果没有上述的第一导风圈184和第二导风圈185之间形成的导风通道，只是一个常规设计的间隙，则该部分气流会沿着隔板180的壁面进入到风轮内部，其气流方向与隔板180表面一致，这部分气流方向与从圆孔沿着排风风机117的轴线方向进入的气流方向大致呈垂直方向，因此二者在间隙处形成冲突干涉，以此形成较大的异音如啸叫声，这会给用户的使用带来干扰。为避免此问题，通过在圆孔处设置第一导风圈184，并在排风风机117的风轮一端设置第二导风圈185，以在这两个导风圈之间形成与风机轴线方向一致的导风通道，如图4所示，当一部分气流如图4中的气流air4，其沿着隔板180表面进入到导风通道后改变方向，形成与进入到排风风机117后的气流air3一致方向，即与排风风机117的轴线方向一致，以此二者不会导致干涉，从而消除了上述因干涉出现的异音，因而提升用户使用时的体验。通过实验，上述的第一间隙和第二间隙选择一个上述提到的合适的间隙范围值，能使得既满足圆孔不与风轮长期运行不产生干涉的情况下，又形成一个合适的导风通道以避免形成气流异音。在本申请的一些实施例中，该值为1.5mm至2.0mm，如取值为1.7mm。
在本申请的一些实施例中，该冷凝器组件还包括形成风道的外壳，外壳有平坦部分的底面，隔板180设置于外壳的中部，以将外壳内所在的腔体分为进风段188和出风段189。如图3至图9所示，外壳包覆于冷凝器组件的表面，具有平坦的底面，方便安装冷凝换热器106和排风风机117，隔板180将外壳内的腔体分隔为两部分即并列的进风段188和出风段189。其外壳具体包括如图8所示的包覆冷凝换热器106侧的第一外壳186，以及图9所示的包覆排风风机117侧的第二外壳187。
其中排风风机117为离心风机，离心风机有气流排出区域，以及离心风机与外壳内壁面之间的气流回转区域，气流回转区域与气流排出区域的气流存在相反的分量。如图7所示，离心风机在高速旋转时，其风轮的叶片将从圆孔沿风机的轴线方向吸入的气流沿着风轮旋转方向，不断的排放至风轮与冷凝排风口104之间的区域，这其中大部分的气流如图7中的气流air5输送至冷凝排风口104之外，因此区域为气流排出区域，因为缺乏蜗舌结构，也有一小部分的气流会继续沿着风轮被回转至风轮与第二外壳187内壁面之间的区域，如图7中的气流air6，此区域为气流回转区域，气流回转区域的气流与气流排出区域的气流流动方向包含相反的成分，以此使得气流回转区域的一部分气流会从沿着第一导风圈184和第二导风圈185之间的导风通道重新进入到风轮内部，以此减少了此区域的气流沿着背离冷凝排风口104的排风方向冲击第二外壳187内壁面导致的扰流，从而引起噪音问题，使得气流回转区域的干扰气流通过导风通道被吸收，因而能够进一步的降低气流的噪音。
在本申请的一些实施例中，如图7所示，外壳的出风段189即第二外壳187所在腔体在上下方向对称设置，排风风机117的风机轴线靠近或者位于出风段189的对称线，且排风风机117设置于远离出风段189的排风口的一侧，出风段189的上下壁面从风机轴线对应的位置朝向冷凝排风口104逐渐缩小至冷凝排风口104大小，出风段189在冷凝排风口104处的腔室高度为在排风风机117风机轴线处的腔室高度的1/2至4/5；出风段189的一端封闭，另一端设置冷凝排风口104。其中出风段189的对称线为图7中的L1，具体如图7和图9所示，外壳的出风段189即第二外壳187包括两部分，在前端为弧形的半圆状，如图7所示的剖面视图，从穿过排风风机117的轴心C1且垂直于对称线L1形成的分界线L2开始的位置为后端，其后端从分界线L2开始至冷凝排风口104，其上下壁面逐渐缩小最后至冷凝排风口104大小，在前端的弧形段适配排风风机117的形状，后端的渐缩段使得气流排出区域的气流逐渐被压缩，以增大从冷凝排风口104排出的气流流速以向后排放至较远处，因为冷凝入风口105与冷凝排风口104在外壳的后端并列排布，二者相距较近，从冷凝排风口104排出的较高速度的气流有助于减少直接进入到冷凝入风口105的机会，降低二者的气流干涉提升冷凝换热器106的换热能力。为了设置一个合适的渐缩段的结构尺寸以对气流形成合理的加速效应，如图7中所示，第二外壳187在冷凝排风口104处的高度为H1，在分界线L2处即在排风风机117轴线对应位置的高度为H2，其中H1与H2的比列范围1/2至4/5即0.5至0.8范围，优选地，该范围值可进一步取值为0.55至0.75，如图7中的比例值为0.61。
本申请还提出一种便携式空调器，如图1至图10所示，包括底板142和与底板142连接的壳体199，在壳体199的前侧设置有斜向上的蒸发出风口102以及与蒸发出风口102靠近的蒸发进风口103，在壳体199的后部设置有上述的冷凝器组件，壳体199和底板142为长条形设置，从前到后设置有蒸发换热器109、压缩机107和冷凝换热器106，蒸发换热器109、压缩机107和冷凝换热器106之间通过冷媒管路连接，以此形成制冷系统。如图1、图3和图7所示，蒸发进风口103、蒸发换热器109和进风风机108的风轮大致竖直且平行排布，蒸发出风口102向上倾斜，其位于进风风机108的斜上方，以此形成从进风至出风大致V型风路通道，使得这几个部件排布紧凑，整体占用的空间少，而斜向上的蒸发出风口102能避免其出风和进风的干涉，即避免蒸发出风口102排出的冷风直接被吸入到蒸发进风口103内造成对周围环境制冷效果的下降。通过将空调器的壳体199设置为长条形，相对市面上常见的竖直外形的移动空调器，其空调器高度大大降低且底部面积增加，有利于放置得平稳降低翻倒的风险，以此方便携带。且包括蒸发换热器109在内的制冷循环部件与包括冷凝换热器106在内的制热循环部件分别设置在压缩机107的两侧，使得整个空调器的重心分布均匀，更加适宜方便携带。在空调器的壳体的上表面可设置把手101件，以此通过握持把手101可轻松的将整个空调器稳定的提起来进行搬运。
在一些实施例中，如图10所示，在底板142上还设置有接水盘162，该接水盘162有设置在蒸发换热器109下的第一接水段1621，该接水盘162从前向后倾斜设置，该接水盘162位于底板142以上，且和底板142之间存在间隔。其中接水盘162的四周为竖直的壁面，以此形成容水的腔体，以此通过设置接水盘162，并将接水盘162的第一接水段1621安装在蒸发换热器109下方，从而收集空调器制冷时蒸发换热器109产生的冷凝水，避免冷凝水直接流到底板142上，而且将接水盘162和底板142上存在一定间距，如设置间距为0.5cm至5cm，以此使得接水盘162和底板142之间存在空气间隔，从而使得接水盘162上的冷凝水的低温不会传递到底板142上，因而不会使得底板142温度降低产生凝露现象，即使在接水盘162的外表面产生凝露，其凝露产生的小水珠的水量相对冷凝水要少很多，即使滴落到底板142上，其非常少量的水会被温度相对高的底板142蒸发掉，不会对底板142的温度产生实质性的降温。而且接水盘162设置为从蒸发换热器109的前侧向冷凝换热器106的后侧倾斜，从而使得蒸发换热器109滴落的冷凝水能被接水盘162快速的流走，而不会在第一接水段1621的位置集聚导致外溢现象。
在本申请的一些实施例中，接水盘162还包含第二接水段1622，该接水段为窄片状，其设置在冷媒管路下，该冷媒管路为连接压缩机107吸气管至蒸发换热器109的管路具体为图3中所示的冷媒管连接段164。根据空调器的工作原理，从压缩机107的排气口出来冷媒管中为高温高压的气态冷媒，经过冷凝换热器106向外排放热量以对冷媒管路中的冷媒进行冷却后，变成低温高压的液态冷媒，并经节流降压部件如毛细管163节流降压后成为温度稍低的中温高压液态冷媒，再进入蒸发换热器109，经蒸发换热器109对周围环境吸热以降温，其冷媒温度升高，而贯穿蒸发换热器109中的冷媒管中的温度非常低，使得安装于冷媒管的蒸发换热器109的翅片的温度也同样非常低，因而产生冷凝水，滴落至蒸发换热器109下方的接水盘162的第一接水段1621，从蒸发换热器109出来后变成低温的气态冷媒，最后进入压缩机107的吸气口再由压缩机107对气态冷媒进行压缩成高温高压冷媒，如此循环。因此连接蒸发换热器109的入口和出口的冷媒管也会对外进行吸热使得冷媒管的温度很低，一般低于2°以下，因此这段冷媒管也会容易产生冷凝水，特别是连接压缩机107的吸气口的冷媒管即冷媒管连接段164，而连接蒸发换热器109和冷凝换热器106之间的冷媒管由于主要为毛细管163，其管径相对其他位置的冷媒管要小很多，因此产生的冷凝水少很多，不易滴落。因而首选需要将连接压缩机107的吸气口的冷媒管即冷媒管连接段164设置于接水盘162上方，即设置于第二接水段1622的上方，以此承接滴落的冷凝水。在本申请的一些实施例中，将连接蒸发换热器109和冷凝换热器106之间的冷媒管段即毛细管163也同时设置于第二接水段1622的上方，以此降低其产生的冷凝水滴落到接水盘162上的现象。
在本申请的一些实施例中，在底板142上设置了若干个固定块165，接水盘162安装在这些固定块165之上，具体在第一接水段1621下有一个与之形状适配的长条形固定块165，在第二接水段1622下有两个面积较小的方形固定块165，并可在这些固定块165上的其中一个或者全部设置用于固定接水盘162的结构，如固定柱，以此方便通过固件件如螺钉将接水盘162固定于固定块165上。
在本申请的一些实施例中，第二接水段1622有形成尾部开口的围框，该围框包括竖向设置的立筋，以及水平沿底板142两侧延伸的水平筋。其中第一接水段1621形成四周竖直壁面的容水腔体，该接水段成左右方向的长条形设置，以与蒸发换热器109的底面适配，而与之连接的第二接水段1622呈前后方向的长条形设置，其两侧设置有由立筋形成的竖直壁面，其底部为沿底板142前后方向的两侧延伸的水平筋，且立筋向下延伸与水平筋一体连接，以形成围框，第二接水段1622的走向与第一接水段1621大致呈直角，在立筋的位于后部的一端设置有与底板142的后部的连接结构，具体为设置于靠近水平筋且位于两侧立筋的固定耳171，其固定耳171中间设置螺钉孔，在底板142上对应位置设置有固定柱，以通过螺钉将固定耳171固定于固定柱上从而将第二接水段1622固定于底板142上。
在底板142位于冷凝换热器106的下方还设置有由四周的竖直壁面围合而成的集水腔168，该集水腔168的一侧与第二接水段1622连接，以收集从第二接水段1622流出的冷凝水，集水腔168设置于冷凝换热器106下方，其目的在于利用空调器工作时冷凝换热器106温度相对环境温度较高，而对集水腔168中的水起到一定的蒸发作用，以降低其水位，且在集水腔168位于底板142的后端还设置有排水孔167，其排水孔167在正常工作时通过橡胶塞堵住，在用户需要排水时将橡胶塞拔出，以实现将集水腔168中的水排放掉，或者进一步可设置排水管（图中未示出）与排水孔167连接，以将集水腔168中的水排放至较远的位置，如可将排水管的另一端放置在体积较大的盛水桶中，以持续的承接集水腔168中的冷凝水。
在本申请的一些实施例中，壳体199上设置有把手件101，在底板142上位于集水腔168的另一侧设置有挡水筋166以形成隔水区域，在壳体199内位于隔水区域所在位置安装有电控盒161，把手件101设置于壳体199的上方，以便于握持把手件101将空调器提携。在把手件101所在壳体199的前后部，压缩机107安装于底板142的靠近中心位置，电控盒161与第二接水段1622分别设置于压缩机107的两侧，为了防止电控盒161下方的底板142上积水使得积水较高时进入电控盒161内部引起电控盒161内部的电路板短路从而引起空调器故障，在电控盒161下方的底板142区域应该尽量保持干燥，因而在安装排风风机117的区域进一步设置挡水筋166，以此避免集水腔168溢出的水扩散到电控盒161下方区域，从而保证了电控盒161内部电控板工作的安全性。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本申请的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不一定指的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任何的一个或多个实施例或示例中以合适的方式结合。
在本申请的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“长度”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”“内”、“外”、“顺时针”、“逆时针”、“轴向”、“径向”、“周向”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本申请和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本申请的限制。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。在本申请的描述中，“多个”的含义是至少两个，例如两个，三个等，除非另有明确具体的限定。
需说明的是，当部件被称为“固定于”或“设置于”另一个部件，它可以直接在另一个部件上或者间接在该另一个部件上。当一个部件被称为是“连接于”另一个部件，它可以是直接或者间接连接至该另一个部件上。
在本申请中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固定”等术语应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系，除非另有明确的限定。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本申请中的具体含义。
在本申请中，除非另有明确的规定和限定，第一特征在第二特征“上”或“下”可以是第一和第二特征直接接触，或第一和第二特征通过中间媒介间接接触。而且，第一特征在第二特征“之上”、“上方”和“上面”可是第一特征在第二特征正上方或斜上方，或仅仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”可以是第一特征在第二特征正下方或斜下方，或仅仅表示第一特征水平高度小于第二特征。
尽管上面已经示出和描述了本申请的实施例，可以理解的是，上述实施例是示例性的，不能理解为对本申请的限制，本领域的普通技术人员在本申请的范围内可以对上述实施例进行变化、修改、替换和变型。凡在本申请的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本申请的权利要求范围之内。

Claims (10)

  1. 一种冷凝器组件，包括排风风机、进风段和出风段，其特征在于，所述进风段设置有冷凝换热器，所述出风段设置有所述排风风机，所述进风段的排风风向与所述出风段的进风风向相反，且所述进风段与所述出风段间隔设置于隔板的两侧；
    所述冷凝换热器与进风方向的夹角为15°至45°设置，以形成楔形的进风腔。
  2. 根据权利要求1所述的冷凝器组件，其特征在于，所述进风腔与所述进风段的入风口之间设置有扩口段；所述冷凝换热器与所述排风风机之间形成有倒楔形的静压腔，所述冷凝换热器的翅片梳理空气从所述进风段进入所述静压腔，所述静压腔通过所述隔板上的排气口连接至所述排风风机的吹风区域。
  3. 根据权利要求2所述的冷凝器组件，其特征在于，所述排气口为用于排气的圆孔，所述圆孔处向所述排风风机的方向延伸出渐缩的第一导风圈，该第一导风圈形成圆筒形排出口。
  4. 根据权利要求3所述的冷凝器组件，其特征在于，所述排风风机向所述圆孔方向对应延伸出渐缩的第二导风圈，该第二导风圈套设在所述第一导风圈外围，并与所述第一导风圈形成环状的第一间隙，且第二导风圈的自由端与所述隔板对应位置形成第二间隙，所述第一间隙范围为1.0mm至3.0mm，所述第二间隙范围为1.0mm至3.0mm。
  5. 根据权利要求1所述的冷凝器组件，其特征在于，还包括形成风道的外壳，所述外壳有平坦部分的底面，所述隔板设置于所述外壳的中部，以将所述外壳内所在的腔体分为进风段和出风段。
  6. 根据权利要求5所述的冷凝器组件，其特征在于，所述排风风机为离心风机，所述离心风机有气流排出区域，以及所述离心风机与所述外壳内壁面之间的气流回转区域，所述气流回转区域与气流排出区域的气流存在相反的分量。
  7. 根据权利要求5所述的冷凝器组件，其特征在于，所述外壳的出风段在上下方向对称设置，所述排风风机的风机轴线靠近或者位于所述出风段的对称线，且所述排风风机设置于远离出风段的冷凝排风口的一侧，所述出风段的上下壁面从所述风机轴线对应的位置朝向所述冷凝排风口逐渐缩小至所述冷凝排风口大小，所述出风段在所述冷凝排风口处的腔室高度为在所述风机轴线处的腔室高度的1/2至4/5；所述出风段的一端封闭，另一端设置所述冷凝排风口。
  8. 一种便携式空调器，其特征在于，包括底板和与底板连接的壳体，在壳体的前侧设置有斜向上的蒸发出风口以及与蒸发出风口靠近的蒸发进风口，在壳体的后部设置有如权利要求1至7任意一项所述的冷凝器组件，所述的壳体和底板为长条形设置，从前到后设置有蒸发换热器、压缩机和冷凝换热器，所述蒸发换热器、压缩机和冷凝换热器之间通过冷媒管路连接。
  9. 如权利要求8所述的便携式空调器，其特征在于，在所述底板上还设置有接水盘，所述接水盘与所述底板之间存在间隔，所述接水盘包括设置在所述蒸发换热器写的第一接水段和设置在冷媒管路段下的第二接水段，其中所述冷媒管路为连接压缩机吸气管至所述蒸发换热器的所述冷媒管路。
  10. 如权利要求9所述的便携式空调器，其特征在于，所述底板的位于冷凝换热器的下方还设置有集水腔，所述集水腔由四周的竖直壁面围合而成，所述集水腔的一侧与所述第二接水段连接，以收集从所述第二接水段流出的冷凝水；所述集水腔位于底板的后端还设置有排水孔；或在所述集水腔上还设置有打水轮，以将冷凝水打水至所述冷凝换热器的翅片的表面。
PCT/CN2021/104264 2020-07-03 2021-07-02 冷凝器组件和便携式空调器 WO2022002253A1 (zh)

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