WO2020103579A1 - 空调室内机和空调器 - Google Patents

空调室内机和空调器

Info

Publication number
WO2020103579A1
WO2020103579A1 PCT/CN2019/109140 CN2019109140W WO2020103579A1 WO 2020103579 A1 WO2020103579 A1 WO 2020103579A1 CN 2019109140 W CN2019109140 W CN 2019109140W WO 2020103579 A1 WO2020103579 A1 WO 2020103579A1
Authority
WO
WIPO (PCT)
Prior art keywords
air
indoor unit
air conditioner
conditioner indoor
wind wheel
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/CN2019/109140
Other languages
English (en)
French (fr)
Inventor
刘乾坤
王锡栋
凌敬
邹奎芳
覃强
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.)
Midea Group Co Ltd
GD Midea Air Conditioning Equipment Co Ltd
Original Assignee
Midea Group Co Ltd
GD Midea Air Conditioning Equipment Co Ltd
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 Midea Group Co Ltd, GD Midea Air Conditioning Equipment Co Ltd filed Critical Midea Group Co Ltd
Publication of WO2020103579A1 publication Critical patent/WO2020103579A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
    • 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
    • F24F13/24—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
    • F24F13/28—Arrangement or mounting of filters
    • 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
    • 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 conditioning, in particular to an air conditioner indoor unit and an air conditioner.
  • the main purpose of the present application is to provide an indoor unit of an air conditioner, which aims to make the air intake resistance during the operation of the air conditioner indoor unit small, the air output more stable, and improve the surge phenomenon.
  • the air conditioner indoor unit proposed by the present application includes a cabinet, the cabinet is provided with an air inlet and an air outlet, and an air duct connecting the air inlet and the air outlet is formed, and the air duct is provided with There is a wind wheel and an evaporator surrounding the outside of the wind wheel;
  • the projection of the wind wheel on the horizontal plane falls in the front-rear direction into the projection range of the air inlet on the horizontal plane;
  • said air inlet in a horizontal plane in the projection length in the longitudinal direction L in, the outer diameter of the rotor is D 2, L in at least not less than 1.5D 2.
  • the distance between the projection of the front side of the wind wheel on the horizontal plane and the projection of the front side of the air inlet on the horizontal plane is greater than 0.5D 2 .
  • the cabinet includes an upper wall of the air duct and a lower wall of the air duct, and an air duct is formed between the upper wall of the air duct and the lower wall of the air duct;
  • the upper wall of the air duct includes an upper wall connecting section and a front volute, the front volute is formed by bending from an end of the upper wall connecting section near the air inlet, and the front volute extends toward the air inlet;
  • the lower wall of the air duct includes a lower wall connecting section and a rear volute, and the rear volute extends from an end of the lower wall connecting section near the air inlet toward the air inlet.
  • the minimum distance between the upper wall of the air duct and the lower wall of the air duct is L out , and L out is at least 0.42D 2 and not more than 0.57D 2 .
  • the upper wall connection section and the lower wall connection section are oppositely arranged, and the upper wall connection section and the lower wall connection section intersect along an extension line extending away from the wind outlet direction to form a diffusion angle ⁇ ,
  • the value range of the diffusion angle ⁇ is: ⁇ is at least greater than 0 ° and not more than 180 °.
  • the value range of the diffusion angle ⁇ is: ⁇ is at least not less than 5 ° and not more than 25 °.
  • the length of the lower wall connecting section is L 3 , and L 3 is at least not less than 0.15D 2 .
  • the distance between the wind wheel and the front volute is ⁇ 1 , and ⁇ 1 is at least not less than 0.035D 2 and not more than 0.065D 2 .
  • the value range of the distance ⁇ 1 between the wind wheel and the front volute is: ⁇ 1 is at least not less than 3.0 mm.
  • the distance between the wind wheel and the rear volute is ⁇ 2
  • ⁇ 2 is at least not less than 0.035D 2 and not more than 0.065D 2 .
  • the value range of the distance ⁇ 2 between the wind wheel and the rear volute is: ⁇ 2 is at least not less than 3.0 mm.
  • a line connecting the center of the wind wheel to the nearest point of the front scroll tongue and a line connecting the center of the wind wheel to the closest point of the rear scroll tongue is the wind outlet arc angle ⁇ , which is at least not less than 160 ° and not more than 185 °.
  • the chassis includes a chassis, a face frame, and a front panel, the front panel is connected to the front side of the face frame, the chassis is connected to the rear side of the face frame, and the lower end of the chassis is formed
  • the lower end of the face frame is formed as the upper wall of the air duct
  • the air inlet is located at the top of the face frame
  • the air outlet is located at the lower portion of the face frame.
  • the evaporator includes a front steaming section between the wind wheel and the front panel, and a distance between the front steaming section and the front panel is L 4 , and L 4 is at least not less than 0.2D 2 .
  • the evaporator further includes a middle steaming section and a rear steaming section, the front steaming section, the middle steaming section and the rear steaming section are connected in sequence, and the middle steaming section and the rear steaming section One end is connected above the wind wheel, the end of the rear steaming section facing away from the middle steaming section extends toward the rear side of the wind wheel, and the end of the middle steaming section facing away from the rear steaming section faces The wind wheel extends in the front direction.
  • the indoor unit of the air conditioner further includes a filter screen, the filter screen is disposed in the air duct and is located between the air inlet and the evaporator.
  • the air conditioner indoor unit further includes an inlet grille, and the casing is installed with the inlet grille at the air inlet.
  • the air conditioner indoor unit further includes electric auxiliary heat, and the electric auxiliary heat is installed in the air duct.
  • This application also proposes an air conditioner, including an outdoor air conditioner and the indoor air conditioner;
  • the air conditioner indoor unit includes a cabinet, the cabinet is provided with an air inlet and an air outlet, and an air duct connecting the air inlet and the air outlet is formed, the air duct is provided with a wind wheel, and the surrounding Evaporator outside the wind wheel;
  • the projection of the wind wheel on the horizontal plane falls in the front-rear direction into the projection range of the air inlet on the horizontal plane;
  • said air inlet in a horizontal plane in the projection length in the longitudinal direction L in, the outer diameter of the rotor is D 2, L in at least not less than 1.5D 2.
  • the projection of the wind wheel on the horizontal plane falls into the projection range of the air inlet on the horizontal plane in the front and rear directions, and the projection of the air inlet on the horizontal plane and the length L in in the front and rear directions are set to be greater than or equal to 1.5
  • the outer diameter of the wind wheel is doubled.
  • the size of the air inlet in the front and rear directions matches the outer diameter of the wind wheel.
  • the outside air can enter the air duct from the air inlet more smoothly.
  • the resistance of the air flow is reduced, the amount of air intake is increased, the working efficiency of the wind wheel is improved, and the heat exchange efficiency of the evaporator is improved, thereby improving the cooling and heating effects of the air conditioner.
  • the amount of air entering the air duct from the air inlet is more uniform, and the stability of the air blown out of the air outlet is improved. Even during long-term use, the air conditioner can still maintain a high operating efficiency, which can improve the surge of the air conditioner during long-term use. phenomenon.
  • FIG. 1 is a schematic cross-sectional view of an embodiment of an air-conditioning indoor unit of the present application
  • Fig. 2 is a partially enlarged view at II in Fig. 1;
  • Figure 3 is a partial enlarged view of the position III in Figure 1;
  • FIG. 4 is a schematic cross-sectional view of the plan A of the air-conditioning indoor unit of the present application.
  • FIG. 5 is a velocity cloud diagram of scheme A in FIG. 4;
  • FIG. 6 is a trace diagram of scheme A in FIG. 4;
  • FIG. 7 is a schematic cross-sectional view of the plan B of the air-conditioning indoor unit of the present application.
  • FIG. 8 is a velocity cloud diagram of scheme B in FIG. 7;
  • Figure 10 is a comparison diagram of the relative velocity distribution of each monitoring point of Scheme A and Scheme B;
  • Fig. 11 is a schematic diagram of the change curve of air volume and noise between the wind wheel and the base of the tongue at ⁇ 1 and the distance between the wind wheel and the rear volute at ⁇ 2 ;
  • Fig. 13 is a graph of the rotation speed of the wind wheel in plan C and plan D corresponding to the air volume in the duct;
  • FIG. 14 is a graph of the rotation speed of the wind turbine in plan C and plan D versus the power of the wind turbine;
  • FIG. 15 is a graph of the rotation speed of the wind wheel in plan C and plan D versus noise.
  • first, second, etc. are for descriptive purposes only, and cannot be understood as indicating or implying their relative importance or implicitly indicating the number of technical features indicated.
  • the features defined with “first” and “second” may include at least one of the features either explicitly or implicitly.
  • the technical solutions between the various embodiments can be combined with each other, but they must be based on the ability of those skilled in the art to realize. When the combination of technical solutions contradicts or cannot be realized, it should be considered that the combination of such technical solutions does not exist , Nor within the scope of protection required by this application.
  • the present application proposes an air conditioner indoor unit 100, which includes a cabinet 10, which is provided with an air inlet 131 and an air outlet 133, and an air duct connecting the air inlet 131 and the air outlet 133 is formed. Inside, a wind wheel 18 and an evaporator 17 surrounding the outside of the wind wheel 18 are provided.
  • the air-conditioning indoor unit 100 in the technical solution of the present application is mainly a wall-mounted air-conditioning indoor unit 100 or a cabinet-type air-conditioning indoor unit 100.
  • the technical solution of the present application is mainly based on the positional relationship of the wall-mounted air-conditioning indoor unit 100 after the installation is completed It can be understood that when the air-conditioning indoor unit 100 is a cabinet, the relative positional relationship of its structure meets the limitations of the technical solution of the present application, and only the overall orientation of the air-conditioning indoor unit 100 as defined in the present application needs to be adjusted. Within the scope of protection of this application.
  • the wall-mounted air conditioner indoor unit 100 has a use state when the installation is completed. In this use state, the rear side of the cabinet 10 is installed on the installation carrier through the installation plate. At this time, the direction perpendicular to the installation surface can be defined as the front-rear direction , And define that the direction perpendicular to the front-rear direction in the same horizontal plane is the left-right direction, and the direction perpendicular to the horizontal plane is defined as the up-down direction. Normally, the wall-mounted air conditioner indoor unit 100 has the largest dimension in the left-right direction. It can be understood that when the wall-mounted air conditioner indoor unit 100 is in a non-use state, the front-back direction, the up-down direction, and the left-right direction are defined accordingly according to the use state.
  • the projection of the wind wheel 18 on the horizontal plane falls in the front-rear direction into the projection range of the air inlet 131 on the horizontal plane;
  • the air inlet 131 in the horizontal plane in the projection length in the longitudinal direction L in, the outer diameter of the rotor 18 is D 2, L in at least not less than 1.5D 2.
  • the air driven by the wind wheel 18 enters the air passage from the air inlet 131, and is sent out through the air outlet 133 after heat exchange by the evaporator 17, during this process, the positional relationship between the air inlet 131 and the wind wheel 18 and the air inlet
  • the size of the air outlet 131 and the wind wheel 18 directly affects the amount of air intake in the air duct, and the direction and velocity of the air flow after entering the air duct.
  • the projection of the wind wheel 18 on the horizontal plane falls in the front-rear direction into the projection range of the air inlet 131 on the horizontal plane, and the length L in of the projection of the air inlet 131 on the horizontal plane and the front-rear direction is set to be greater than or equal to 1.5 times the outer diameter of the wind wheel 18.
  • the size of the air inlet 131 in the front-rear direction matches the outer diameter of the wind wheel 18.
  • the outside air can flow more smoothly from the air inlet 131 Entering the air duct, the air flow resistance of the air duct is reduced, the air intake is increased, the working efficiency of the wind wheel 18 is improved, and the heat exchange efficiency of the evaporator 17 is improved, thereby improving the cooling and heating effects of the air conditioner.
  • the air volume entering the air duct from the air inlet 131 is more uniform, and the stability of the air blown out of the air outlet 133 is improved. Even during long-term use, the air conditioner can still maintain a high operating efficiency, which can improve the air conditioner during long-term use. Surge phenomenon.
  • the distance between the projection of the front side of the wind wheel 18 on the horizontal plane and the projection of the front side of the air inlet 131 on the horizontal plane is greater than 0.5D 2 .
  • the intersection point of the cross section of the air conditioner indoor unit 100 and the axis of the wind wheel 18 is defined as O, and the first auxiliary straight line is defined.
  • the first auxiliary straight line passes through the point O and extends in the front-rear direction.
  • the first auxiliary straight line and the wind The front side of the wheel 18 intersects at point B, and the rear side of the wind wheel 18 intersects at point A.
  • the first auxiliary straight line extends from point B to the direction away from point A to form point C.
  • the length from point A to point C is greater than or equal to 1.5 D 2 , the projection of points A to C on the horizontal plane falls within the projection range of the air inlet 131 on the horizontal plane.
  • the direction of the air duct is biased to the front side of the wind wheel 18, therefore, the center position of the air inlet 131 is biased to the front side of the wind wheel 18, so that the wind wheel 18 has a better air intake effect.
  • the efficiency of the wind wheel 18 is further improved.
  • the evaporator 17 includes a front steaming section 171, a middle steaming section 173 and a rear steaming section 175 connected in sequence, one ends of the middle steaming section 173 and the rear steaming section 175 are connected above the wind wheel 18, and the rear steaming section 175 faces away
  • One end of the middle steaming section 173 extends toward the rear side of the wind turbine 18, and one end of the middle steaming section 173 facing away from the rear steaming section 175 extends toward the front side of the wind turbine 18.
  • This embodiment mainly improves the size of the wind speed before and after the evaporator 17, improves the distribution of the overall speed during the exchange of air and the evaporator 17, improves the uniformity of the airflow in the air duct, and is beneficial to improving surge and further improving heat exchange efficiency.
  • this application has conducted simulation analysis for two different sizes of the air inlet 131.
  • FIG. 4 shows the air-conditioning indoor unit 100 of solution A
  • FIG. 6 shows the air-conditioning indoor unit 100 of solution B
  • the wind wheel 18 of the air-conditioning indoor unit 100 is a cross-flow wind wheel
  • the outer diameter D of the wind wheel 18 2 are 98mm
  • 16U tube evaporator 17 to evaporator 17 -D7 window sheet FIG. 4 and FIG. 5 for convenience of experimental data were analyzed
  • the evaporator 17 is arranged in the monitoring points 17 from back to front , 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13, 14, 15, 16, and 17, respectively.
  • Figures 5 and 6 respectively give the velocity cloud and trace of the simulation results of Scheme A
  • Figures 7 and 8 respectively give the velocity cloud and trace of the simulation results of Scheme B
  • the unit of wind speed in the velocity cloud is m / s. The darker the gray, the greater the velocity of air in the air duct.
  • the curves with arrows represent the trajectory of air flowing from the air inlet 131 to the air outlet 133.
  • the corner vortex 191 disappears at the air inlet 131.
  • the average speed of the windward surface upstream of the evaporator 17 increases, and the coverage area of the low-speed area decreases; meanwhile, the cross-flow wind wheel 18 is eccentric
  • the vortex 192 is away from the center of the wind wheel 18 and the size is reduced.
  • the solution A that is, the improved solution of the present application, can significantly improve the size and direction of the air flow in the air duct and the uniformity of the air flow in the air duct, and improve the wind output efficiency of the wind wheel 18.
  • the relative velocity distributions of the 17 monitoring points upstream of the evaporator 17 in Scheme A and Scheme B are given.
  • the wind speed at each monitoring point is V
  • the wind speed V max at the maximum wind speed point among all monitoring points is taken as a reference.
  • the relative speed of each monitoring point is defined as V / V max . It can be seen from the figure that in Scheme B, the relative speeds of the monitoring points 1 and 2 near the monitoring points 14, 15, 16, 17 near the front steaming section 171 and the lower half of the rear steaming section 175 decrease, and the middle steaming section 173 and the post-steaming section
  • the relative speeds of the monitoring points 3 ⁇ 13 near the upper part of 175 increase.
  • the uniformity of wind speed in Option B deteriorates, the overall heat exchange efficiency of the evaporator 17 decreases, and the stability of the air outlet also deteriorates.
  • the air duct system Increased risk of surge. It can be seen that in the improved scheme A, the wind speed in the air duct is uniform, the overall heat exchange efficiency of the evaporator 17 is improved, the air output is more stable, and the risk of surge in the air duct system is reduced.
  • the cabinet 10 includes an air duct upper wall 135 and an air duct lower wall 111, and an air duct is formed between the air duct upper wall 135 and the air duct lower wall 111;
  • the upper wall 135 of the air duct includes an upper wall connecting section 1351 and a front volute tongue 1353.
  • the front volute tongue 1353 is bent from an end of the upper wall connecting section 1351 close to the air inlet 131, and the front volute tongue 1353 faces the air inlet 131 extend;
  • the lower wall 111 of the air duct includes a lower wall connecting section 1111 and a rear volute tongue 1113.
  • the rear volute tongue 1113 extends from an end of the lower wall connecting section 1111 near the air inlet 131 toward the air inlet 131.
  • the air entering the air duct from the air inlet 131 is guided by the upper wall 135 of the air duct and the lower wall 111 of the air duct, and then passes through the area surrounded by the front volute tongue 1353 and the rear volute tongue 1113, and then passes through the upper wall connecting section 1351
  • the area connected to the lower wall 1111 is delivered to the air outlet 133.
  • the minimum distance between the upper wall 135 of the air duct and the lower wall 111 of the air duct is L out , and L out is at least 0.42D 2 and not more than 0.57D 2 .
  • the minimum distance between the upper wall 135 of the air duct and the lower wall 111 of the air duct determines the air volume of the air-conditioning indoor unit 100 and the static pressure at the air outlet 133.
  • the minimum distance between the air ducts is L out , L out is at least 0.42D 2 and does not More than 0.57D 2 .
  • the minimum distance between the upper wall 135 of the air channel and the lower wall 111 of the air channel is also the minimum distance between the air outlet channels. If the minimum distance L out is less than 0.42D 2 , the wind range will be reduced and the efficiency of the air outlet will be reduced. If the minimum distance L out is greater than 0.57D 2 , the intensity of the outflow will be reduced and the air supply distance will be shorter.
  • the minimum interval L out of the air outlet duct is limited to the range of 0.42D 2 to 0.57D 2 , which can ensure that the wind energy sent from the air outlet 133 maintains a certain air supply distance, and ensures the comfort of cooling and heating the room.
  • the upper wall connection section 1351 and the lower wall connection section 1111 are oppositely arranged, and the upper wall connection section 1351 and the lower wall connection section 1111 intersect along an extension line extending away from the wind direction to form a diffusion angle ⁇ , a diffusion angle
  • ⁇ a diffusion angle
  • the value range of ⁇ is: ⁇ is at least greater than 0 ° and not more than 180 °.
  • the distance between the upper wall connecting section 1351 and the lower wall connecting section 111 increases gradually along the direction of the wind, forming a trumpet shape, which can disperse the air in the air duct, not only making the air sent by the air outlet 133 even Good sex, and make the air supply distance longer.
  • the value range of the diffusion angle ⁇ is: ⁇ is at least not less than 5 ° and not more than 25 °. If the diffusion angle ⁇ is less than 5 °, the range of air sent through the air outlet 133 is small; if the diffusion angle ⁇ is greater than 25 °, the range of air sent through the air outlet 133 is too large, which will cause uneven temperature of the air and send The wind distance decreases.
  • the diffusion angle ⁇ takes a value in the range of 5 ° to 25 °, which can ensure a large air outlet 133, and obtain relatively small noise and satisfactory comfort.
  • the length of the lower wall connecting section 1111 is L 3 , and L 3 is at least not less than 0.15D 2 .
  • L 3 is at least not less than 0.15D 2 .
  • L 3 is at least not less than 0.15D 2 .
  • L 3 greater than 0.15D 2 can ensure a certain static pressure of the air duct.
  • the minimum distance L out of the upper wall 135 of the air duct and the lower wall 111 of the air duct is in the range of 0.42D 2 to 0.57D 2
  • the connecting section L 3 of the lower wall of the air outlet 133 is required to be at least not less than 0.15D 2 to ensure the basic performance of the air duct
  • the diffusion angle ⁇ needs to be matched with the length of L 3 Adjustment, when L 3 and ⁇ meet the above value range, when L 3 is smaller, the closer ⁇ is to the upper limit of the value range, it can ensure that there is a larger air outlet 133, the air outlet range is larger, and the air outlet is softer; When L 3 is larger, the closer ⁇ is to the lower limit of the value range, it can prevent the air outlet 133 from flowing back and reduce the stability of the air outlet, while reducing the risk of surge and condensation.
  • the distance between the wind wheel 18 and the front scroll 1353 is ⁇ 1
  • the distance between the wind wheel 18 and the rear scroll 1113 is ⁇ 2 ;
  • ⁇ 1 is at least not less than 0.035D 2 and not more than 0.065D 2 ; and / or, ⁇ 2 is at least not less than 0.035D 2 and not more than 0.065D 2 .
  • Figure 11 shows the relationship between ⁇ 1 and ⁇ 2 and air volume and noise, where the abscissa is ⁇ 1 or ⁇ 2 , and the ⁇ 1 or ⁇ 2 is divided into three intervals, which are A interval, B interval and C interval, respectively , The ordinate is the air volume or noise.
  • ⁇ 1 and ⁇ 2 satisfy: ⁇ 1 is at least not less than 0.035D 2 and not more than 0.065D 2 , and ⁇ 2 is at least Not less than 0.035D 2 and not more than 0.065D 2 .
  • the value range of the distance ⁇ 1 between the wind wheel 18 and the front volute 1353 satisfies: ⁇ 1 is at least not less than 3.0 mm; and / or the wind wheel 18 and The value range of the distance ⁇ 2 of the rear volute 1113 satisfies: ⁇ 2 is at least not less than 3.0 mm. So that the ⁇ 1 and ⁇ 2 are not too small to affect the installation.
  • the cross section of the air conditioner indoor unit 100 is formed by the connection between the center of the wind wheel 18 to the nearest point of the front volute 1353 and the line from the center of the wind wheel 18 to the closest point of the rear volute 1113
  • the angle is the wind exit arc angle ⁇ , ⁇ is at least not less than 160 ° and not more than 185 °.
  • a second auxiliary straight line is defined.
  • the second auxiliary straight line passes through point O and extends perpendicular to the direction of the posterior volute tongue 1113, and intersects with the posterior volute tongue 1113 at point N;
  • the present application provides Scheme C and Scheme D to test the degree to which the distances ⁇ 1 and ⁇ 2 affect the efficiency and noise of the wind wheel 18.
  • FIG. 12 shows the air volume, power and noise values corresponding to the rotation speeds of the wind wheel 18 at 900 rpm, 1000 rpm, 1100 rpm and 1200 rpm in scenario C and scenario D. According to the data results of the graph in FIG. 12, graphs are given respectively The schematic diagram of the air volume curve shown in 13, the schematic diagram of the power curve shown in FIG. 14, and the schematic diagram of the noise curve shown in FIG. 15 can more intuitively reflect the relationship between the air volume, power, and noise values in Scheme A and Scheme B.
  • Plan D has a loss of 6.5% -7.5% at the same speed compared to Plan C, and the power is slightly higher at the same air volume, about 2% -3%, and the noise is 0.6-1.0dBA at the same air volume.
  • the air supply efficiency of the fan is reduced, and the noise is also deteriorated.
  • ⁇ 1 and ⁇ 2 fall within the preferred interval, and in Scheme D, ⁇ 1 and ⁇ 2 are too large and do not fall within the preferred interval.
  • the air conditioner indoor unit 100 satisfies ⁇ 1 at least not less than 0.035D 2 and not more than 0.065D 2 , and ⁇ 2 is at least not less than 0.035D 2 and not more than 0.065D 2 , the air volume of the wind wheel 18 at the same speed increases, the air efficiency increases, and the noise decreases.
  • the chassis 10 includes a chassis 11, a face frame 13, and a front panel 15.
  • the front panel 15 is connected to the front side of the face frame 13
  • the chassis 11 is connected to the rear side of the face frame 13
  • the lower end of the chassis 11 is formed as In the air duct lower wall 111
  • the lower end of the face frame 13 is formed as an air duct upper wall 135
  • the air inlet 131 is located at the top of the face frame 13
  • the air outlet 133 is located at the lower portion of the face frame 13.
  • the air duct of the air-conditioning indoor unit 100 is also provided with a filter and other structures.
  • the air enters the air duct through the air inlet 131, is filtered by the filter, and then exchanges heat with the evaporator 17, and the casing 10 is also provided at the air inlet 131.
  • the inlet grille is installed, which can prevent large objects from entering the air duct by mistake, so as to provide preliminary protection for the structure in the air duct, and the filter screen can further protect the structure in the air duct, and can The air is filtered to make the air sent out at the air outlet 133 more clean and of better quality.
  • Electric auxiliary heat can also be added in the air duct.
  • the electric auxiliary heat can further improve the heating efficiency of the air conditioner.
  • the evaporator 17 includes a front steaming section 171 located between the wind wheel 18 and the front panel 15.
  • the distance between the front steaming section 171 and the front panel 15 is L 4 , and L 4 is at least not less than 0.2D 2 .
  • the distance between the front steaming section 171 and the front panel 15 is limited to be greater than or equal to 0.2D 2 , so that sufficient space is left in front of the front steaming section 171, so that the air flow rate at the front steaming section 171 is increased, and the evaporation is further improved.
  • the overall velocity distribution of the device 17 is uniform, improving surge and heat exchange efficiency. If the distance L 4 between the front steaming section 171 and the front panel 15 is less than 0.2D 2 , the gap between the front steaming section 171 and the front panel 15 is too small, resulting in a poor heat exchange effect at the front steaming section 171 .
  • the present application also proposes an air conditioner including an air conditioner outdoor unit and an air conditioner indoor unit 100.
  • the structure of the air conditioner indoor unit 100 refers to the above embodiments. Since the air conditioner adopts all the technical solutions of all the above embodiments, At least all the effects brought by the technical solutions of the above embodiments will not be repeated here.

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Abstract

一种空调室内机和空调器，其中，空调室内机（100）包括机壳（10），所述机壳（10）开设有进风口（131）和出风口（133），且形成有连通所述进风口（131）和出风口（133）的风道，所述风道内设有风轮（18），以及围设于所述风轮（18）外侧的蒸发器（17）；所述风轮（18）于水平面的投影于前后方向上落入所述进风口（131）于水平面的投影范围内；且所述进风口（131）在水平面的投影于前后方向上的长度为L in，所述风轮（18）的外径为D 2，L in至少不小于1.5D 2。该空调室内机运行过程中进风阻力小、出风更加稳定，改善了喘振现象。

Description

空调室内机和空调器
相关申请
本申请要求2018年11月19日申请的，申请号为201811380197.0名为“空调室内机和空调器”的中国专利申请优先权，在此将其全文引入作为参考。
技术领域
本申请涉及空调技术领域，特别涉及一种空调室内机和空调器。
背景技术
现有空调室内机的风道并没有普遍适用的设计方法或设计准则可以遵循，在使用过程中有些隐性的品质风险很难被发现，比如室内机长期运行后进风阻力大、出风稳定性变差，甚至出现喘振等不良影响。
申请内容
本申请的主要目的是提供一种空调室内机，旨在使得空调室内机运行过程中进风阻力小、出风更加稳定，改善喘振现象。
为实现上述目的，本申请提出的空调室内机，包括机壳，所述机壳开设有进风口和出风口，且形成有连通所述进风口和出风口的风道，所述风道内设有风轮，以及围设于风轮外侧的蒸发器；
所述风轮于水平面的投影于前后方向上落入所述进风口于水平面的投影范围内；
且，所述进风口在水平面的投影于前后方向上的长度为Lin，所述风轮的外径为D2，Lin至少不小于1.5D2。
可选地，所述风轮的前侧于水平面的投影与所述进风口的前侧于水平面的投影距离大于0.5D2。
可选地，所述机壳包括风道上壁和风道下壁，所述风道上壁和风道下壁之间形成出风风道；
所述风道上壁包括上壁连接段和前蜗舌，所述前蜗舌自所述上壁连接段靠近所述进风口的一端折弯形成，所述前蜗舌朝向所述进风口延伸；
所述风道下壁包括下壁连接段和后蜗舌，所述后蜗舌自所述下壁连接段靠近所述进风口的一端朝向所述进风口延伸设置。
可选地，所述风道上壁和风道下壁的最小间距为Lout，Lout至少是0.42D2且不超过 0.57D2。
可选地，所述上壁连接段和所述下壁连接段相对设置，且所述上壁连接段和所述下壁连接段沿背离出风方向延伸的延长线相交形成扩压角θ，所述扩压角θ的取值范围为：θ至少大于过0°且不超过180°。
可选地，所述扩压角θ的取值范围为：θ至少不小于5°且不超过25°。
可选地，所述下壁连接段的长度为L3，L3至少不小于0.15D2。
可选地，所述风轮与所述前蜗舌的间距为δ1，δ1至少不小于0.035D2且不超过0.065D2。
可选地，所述风轮与所述前蜗舌的间距δ1的取值范围为：δ1至少不小于3.0mm。
可选地，所述风轮与所述后蜗舌的间距为δ2，δ2至少不小于0.035D2且不超过0.065D2。
可选地，所述风轮与所述后蜗舌的间距δ2的取值范围为：δ2至少不小于3.0mm。
可选地，所述空调室内机的横截面上，所述风轮的中心至所述前蜗舌最近点的连线与所述风轮的中心至所述后蜗舌最近点的连线所形成的夹角为出风圆弧角β，β至少不小于160°且不超过185°。
可选地，所述机壳包括底盘、面框和前面板，所述前面板连接于所述面框的前侧，所述底盘连接于所述面框的后侧，所述底盘的下端形成为所述风道下壁，所述面框的下端形成为所述风道上壁，所述进风口位于所述面框的顶部，所述出风口位于所述面框的下部。
可选地，所述蒸发器包括位于所述风轮与所述前面板之间的前蒸段，所述前蒸段与所述前面板的间距为L4，L4至少不小于0.2D2。
可选地，所述蒸发器还包括中蒸段和后蒸段，所述前蒸段、所述中蒸段及所述后蒸段依次连接，所述中蒸段和所述后蒸段的一端于所述风轮的上方相连接，所述后蒸段背离所述中蒸段的一端朝向所述风轮的后侧方向延伸，所述中蒸段背离所述后蒸段的一端朝向所述风轮的前侧方向延伸。
可选地，所述空调室内机还包括滤网，所述滤网设于所述风道内，并位于所述进风口和所述蒸发器之间。
可选地，所述空调室内机还包括进风格栅，所述机壳于所述进风口处安装有所述进风格栅。
可选地，所述空调室内机还包括电辅热，所述电辅热安装于所述风道内。
本申请还提出一种空调器，包括空调室外机和所述的空调室内机；
所述空调室内机，包括机壳，所述机壳开设有进风口和出风口，且形成有连通所述进风口和出风口的风道，所述风道内设有风轮，以及围设于风轮外侧的蒸发器；
所述风轮于水平面的投影于前后方向上落入所述进风口于水平面的投影范围内；
且，所述进风口在水平面的投影于前后方向上的长度为Lin，所述风轮的外径为D2，Lin至少不小于1.5D2。
本申请技术方案中，风轮于水平面的投影于前、后方向上落入进风口于水平面的投影范围内，且进风口在水平面的投影与前、后方向上的长度Lin设置为大于或等于1.5倍的风轮外径，该结构下，进风口在前后方向上的尺寸与风轮的外径相配合，在风轮的驱动下，外界空气能更顺利的由进风口进入风道内，风道空气流动的阻力减小，进风量增大，风轮的工作效率提高，蒸发器的换热效率提高，从而能提升空调器的制冷和制热效果。由进风口进入风道内的风量更加均匀，出风口吹出的空气稳定性提高，即使在长期使用过程中，空调器仍能保持较高的运行效率，能改善空调器长期使用过程中出现的喘振现象。
附图说明
为了更清楚地说明本申请实施例的技术方案，下面将对实施例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示出的结构获得其他的附图。
图1为本申请空调室内机一实施例的截面示意图；
图2为图1中Ⅱ处的局部放大图；
图3为图1中Ⅲ处的局部放大图；
图4为本申请空调室内机方案A的截面示意图；
图5为图4中方案A的速度云图；
图6为图4中方案A的迹线图；
图7为本申请空调室内机方案B的截面示意图；
图8为图7中方案B的速度云图；
图9为图7中方案B的迹线图；
图10为方案A和方案B各监测点的相对速度分布 对比图；
图11为风轮与舌根部的间距为δ1，风轮与后蜗舌的间距为δ2，于A区间、B区间和C区间范围内风量和噪声的变化曲线示意图；
图12为本申请空调室内机方案C和方案D中风轮的转速对应的风量、功率和噪声值的图表；
图13为方案C和方案D中风轮的转速对应风道内风量的曲线图；
图14为方案C和方案D中风轮的转速对应风轮功率的曲线图；
图15为方案C和方案D中风轮的转速对应噪声的曲线图。
附图标号说明：
标号 名称 标号 名称
100 空调室内机 1353 前蜗舌
10 机壳 15 前面板
11 底盘 17 蒸发器
111 风道下壁 171 前蒸段
1111 下壁连接段 173 中蒸段
1113 后蜗舌 175 后蒸段
13 面框 18 风轮
131 进风口 191 角隅涡
133 出风口 192 偏心涡
135 风道上壁 193 贯流区
1351 上壁连接段
本申请目的的实现、功能特点及优点将结合实施例，参照附图做进一步说明。
具体实施方式
下面将结合本申请实施例中的附图，对本申请实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本申请的一部分实施例，而不是全部的实施例。基于本申请中的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本申请保护的范围。
需要说明，本申请实施例中所有方向性指示（诸如上、下、左、右、前、后……）仅用于解释在某一特定姿态（如附图所示）下各部件之间的相对位置关系、运动情况等，如果该特定姿态发生改变时，则该方向性指示也相应地随之改变。
另外，在本申请中涉及“第一”、“第二”等的描述仅用于描述目的，而不能理解为指示或暗示其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。另外，各个实施例之间的技术方案可以相互结合，但是必须是以本领域普通技术人员能够实现为基础，当技术方案的结合出现相互矛盾或无法实现时应当认为这种技术方案的结合不存在，也不在本申请要求的保护范围之内。
本申请提出一种空调室内机100，该空调室内机100包括机壳10，机壳10开设有进风口131和出风口133，且形成有连通进风口131和出风口133的风道，风道内设有风轮18，以及围设于风轮18外侧的蒸发器17。
本申请技术方案中的空调室内机100主要为壁挂式空调室内机100，也可以为柜式空调室内机100，本申请技术方案中主要基于壁挂式空调室内机100于安装完成后的位置关系进行描述，可以理解地，当该空调室内机100为柜机时，其结构的相对位置关系满足本申请技术方案的限定，只需要将本申请的所限定空调室内机100整体方位进行调转，也在本申请所保护的范围内。
该壁挂式空调室内机100于安装完成时即具有使用状态，该使用状态下，机壳10的后侧通过安装板安装于安装载体，此时，可以定义垂直于该安装表面的方向为前后方向，并定义在同一水平面内与该前后方向相垂直的方向为左右方向，垂直于水平面的方向定义为上下方向，通常情况下，壁挂式空调室内机100于该左右方向上的尺寸最大。可以理解地，在该壁挂式空调室内机100具有非使用状态时，前后方向、上下方向以及左右方向对其进行的限定均根据使用状态进行相应的调整。
本申请实施例中，风轮18于水平面的投影于前后方向上落入进风口131于水平面的投影范围内；
且，进风口131在水平面的投影于前后方向上的长度为Lin，风轮18的外径为D2，Lin至少不小于1.5D2。
空调室内机100运行时，风轮18驱动空气由进风口131进入风道内部，经蒸发器17换热后，由出风口133送出，该过程中，进风口131和风轮18的位置关系以及进风口131和风轮18的尺寸直接影响风道内的进风量，以及进入风道后气流的流向和流速大小。本申请技术方案中，风轮18于水平面的投影于前后方向上落入进风口131于水平面的投影范围内，且进风口131在水平面的投影与前后方向上的长度Lin设置为大于或等于1.5倍的风轮18外径，该结构下，进风口131在前后方向上的尺寸与风轮18的外径相配合，在风轮18的驱动下，外界空气能更顺利的由进风口131进入风道内，风道空气流动的阻力减小，进风量增大，风轮18的工作效率提高，蒸发器17的换热效率提高，从而能提升空调器的制冷和制热效果。由进风口131进入风道内的风量更加均匀，出风口133吹出的空气稳定性提高，即使在长期使用过程中，空调器仍能保持较高的运行效率，能改善空调器长期使用过程中出现的喘振现象。
参见图1，风轮18的前侧于水平面的投影与所述进风口131的前侧于水平面的投影距离大于0.5D2。
本申请实施例中，定义空调室内机100的横截面与风轮18的轴线交点为O，定义第一辅助直线，第一辅助直线经O点，并沿前后方向延伸，第一辅助直线与风轮18的前侧交汇于B点，与风轮18的后侧交汇于A点，第一辅助直线由B点至远离A点方向延伸形成C点，A点到C点的长度大于或等于1.5D2，A点到C点于水平面的投影落入进风口131于水平面的投影范围内。
定义该横截面上进风口131最前侧的点为E点，进风口131最后侧的点为D点，D点至E点的距离即为Lin，该实施例中，D点在水平面上的投影位于A点在水平面投影的后侧，且D点和A点在前后方向上的距离为L1，L1＞0；E点在水平面上的投影位于C点在水平面投影的前侧，且E点和C点在前后方向上的距离为L2，L2＞0。根据机壳10内部风道的结构，风道的走向偏向风轮18的前侧，因此，将进风口131的中心位置偏向风轮18的前侧，以使风轮18进风效果更好，进一步提高风轮18的效率。
进一步地，蒸发器17包括依次连接的前蒸段171、中蒸段173和后蒸段175，中蒸段173和后蒸段175的一端于风轮18的上方相连接，后蒸段175背离中蒸段173的一端朝向风轮18的后侧方向延伸，中蒸段173背离后蒸段175的一端朝向风轮18的前侧方向延伸。该实施例主要提升了蒸发器17前后的风速大小，改善了空气与蒸发器17交换过程中整体速度的分布，提高了风道内气流的均匀性，有利于改善喘振、进一步提升换热效率。
参见图4和图9，本申请针对两种不同的进风口131尺寸进行了仿真分析。
图4所示为方案A的空调室内机100，图6所示为方案B的空调室内机100，以上两方案中空调室内机100的风轮18均为贯流风轮，风轮18外径D2均为98mm，蒸发器17为16U管-D7开窗片蒸发器17，图4和图5中为了方便对实验数据进行对比分析，在蒸发器17上从后至前布置了17的监测点，分别为1、2、3、4、5、6、7、8、9、10、11、12、13、14、15、16和17。
参见图4，方案A中，进风口131于前后方向的长度为LinA，LinA=161.7mm=1.65D2，该方案中LinA满足Lin至少不小于1.5D2；参见图6，方案B中，进风口131于前后方向的长度为LinB，LinB=142.1mm=1.45D2，该方案中LinB不满足Lin至少不小于1.5D2。
图5和图6，分别给出了方案A仿真结果的速度云图和迹线图；图7和图8分别给出了方案B仿真结果的速度云图和迹线图；图5和图7中，速度云图中风速单位为m/s，灰度越深，代表空气于风道内的流速越大；图6和图8中，带箭头的曲线代表空气从进风口131至出风口133流动的轨迹。
结合图6和图9，经对比可以分析得出：方案B相较于方案A，进风口131附近出现角隅涡191，且角隅涡191区域较大；结合图5和图8，蒸发器17上游迎风面平均速度降低，低速区覆盖面积增大；图8和图9中均示出，贯流风轮18处偏心涡192向风轮18圆心处靠近，且尺寸增大，导致贯流区193减小，空气通流能力降低，从而使得方案B内流场平均速度降低，转速1200rpm的容积流量约降低13%，风轮18效率显著恶化。根据图6所示，方案A中，进风口131处角隅涡191消失，图5所示，蒸发器17上游迎风面平均速度提高，低速区覆盖面积减小；同时，贯流风轮18处偏心涡192远离风轮18的圆心，且尺寸减小。由此可知，方案A，也就是本申请改进后的方案能够明显改善风道内空气流动的大小和方向，以及风道内空气流动的均匀性，提升了风轮18的出风效率。
进一步参见图10，给出了方案A和方案B中蒸发器17上游17个监测点的相对速度分布对比。各监测的风速为V，取所有监测点中风速最大点的风速Vmax作为基准，各监测点相对速度大小定义为V/Vmax。由图示可知，方案B中，前蒸段171附近监测点14、15、16、17以及后蒸段175下半部分附近监测点1、2相对速度减小，中蒸段173及后蒸段175上半部分附近监测点3~13相对速度增大，较方案A来讲，方案B中风速均匀性恶化，蒸发器17整体的换热效率降低，出风稳定性也变差，风道系统喘振风险增加。由此可知，改进后的方案A中，风道内风速均匀，蒸发器17整体的换热效率提高，出风更加稳定，风道系统出现喘振的风险降低。
进一步地，机壳10包括风道上壁135和风道下壁111，风道上壁135和风道下壁111之间形成出风风道；
风道上壁135包括上壁连接段1351和前蜗舌1353，前蜗舌1353自上壁连接段1351靠近所述进风口131的一端折弯形成，所述前蜗舌1353朝向所述进风口131延伸；
所述风道下壁111包括下壁连接段1111和后蜗舌1113，所述后蜗舌1113自所述下壁连接段1111靠近所述进风口131的一端朝向所述进风口131延伸设置。
该实施例中，由进风口131进入风道内的空气在风道上壁135和风道下壁111的导向下，先经过前蜗舌1353和后蜗舌1113所围区域，再经过上壁连接段1351和下壁连接段1111区域，输送至出风口133。
本申请一实施例中，风道上壁135和风道下壁111的最小间距为Lout，Lout至少是0.42D2且不超过 0.57D2。
风道上壁135和风道下壁111的最小间距决定了空调室内机100的出风量以及出风口133处的静压，出风风道的最小间距为Lout，Lout至少是0.42D2且不超过 0.57D2。该风道上壁135和风道下壁111的最小间距也即为出风风道的最小间距，若该最小间距Lout小于0.42D2，会使得出风范围减小，降低出风效率；若该最小间距Lout大于0.57D2，则会使得出风强度降低，送风距离较短。将出风风道的最小间距Lout限定于0.42D2至0.57D2范围内，能够保证由出风口133送出的风能维持一定的送风距离，且确保房间制冷制热的舒适性。
结合图2，上壁连接段1351和下壁连接段1111相对设置，且上壁连接段1351和下壁连接段1111沿背离出风方向延伸的延长线相交，形成扩压角θ，扩压角θ的取值范围为：θ至少大于过0°且不超过180°。
该实施例中，上壁连接段1351和下壁连接段111沿出风方向，间距逐渐增大，组合形成喇叭口状，能将风道内的空气进行发散，不仅使得出风口133送出的空气均匀性好，而且使得送风距离更远。
进一步地，扩压角θ的取值范围为：θ至少不小于5°且不超过25°。若扩压角θ小于5°，经出风口133送出的空气范围较小；若扩压角θ大于25°，经出风口133送出的空气范围过大，会造成出风温度不均匀，且送风距离减小。扩压角θ在5°至25°的范围内取值，可以保证较大的出风口133，获得相对较小的噪声和满意的舒适性。
本申请实施例中，下壁连接段1111的长度为L3，L3至少不小于0.15D2。L3至少不小于0.15D2。当L3的取值较小时，风道内的静压过低，可能会由于风道内压力较大而引起出风过程中噪音较大的现象。L3大于0.15D2能够保证风道有一定的静压，上壁连接段1351和下壁连接段1111沿出风方向延伸的长度越大，同比风量会越大，以使得静压越高，同风量噪声越低，风道性能。
风道上壁135和风道下壁111的最小间距Lout在0.42D2~0.57D2的范围内，要求出风口133下壁连接段L3至少不小于0.15D2，确保风道的基本性能，同时在理论上，L3取值较大时，扩压角θ可适当取区间5°至25°内较小值，为获得更好的出风效果，扩压角θ需配合L3长度适当调整，在L3和θ满足以上取值范围使，当L3较小时，θ越接近取值范围的上限，可以保证有较大的出风口133，出风范围更大，出风更加柔和；当L3较大时，θ越接近取值范围的下限，能够防止出风口133出现回流降低出风稳定性，同时可降低喘振和凝露风险。
结合贯流风轮的基本流动机理、数值仿真和试验结果可知，风轮18与风道的内壁之间的间隙存在一个理想区间，此区间内风轮18的风量较大，同时噪声也相对较低。
一实施例中，风轮18与前蜗舌1353的间距为δ1，风轮18与后蜗舌1113的间距为δ2；
δ1至少不小于0.035D2且不超过0.065D2；且/或，δ2至少不小于0.035D2且不超过0.065D2。
图11中为δ1、δ2与风量和噪声之间的关系，其中横坐标为δ1或δ2，该δ1或δ2划分为三个区间，分别是A区间、B区间和C区间，纵坐标为风量或者噪声，如图所示，在A区间内，δ1和δ2过小，系统阻力增大，同时部分能量转化为噪声，使风机效率降低，噪声升高；在B区间内，δ1和δ2适当，风轮18内部的循环气流减少，风道内贯流区193增大，贯流风轮18的流量和压头增加；在C区间内，δ1和δ2较大，内流区偏心涡192、循环回流区、内回流区等流动区域增大。由于偏心涡192增大，风轮18内部的循环气流增加，贯流区193域减小，从而导致贯流风轮18的流量降低。
根据以上实现数据可知，B区间范围内风量大且噪声小，为优选范围，该B区间内，δ1和δ2满足：δ1至少不小于0.035D2且不超过0.065D2，δ2至少不小于0.035D2且不超过0.065D2。
进一步地，考虑空调器结构装配出现变形、跌落、运输问题，风轮18与前蜗舌1353的间距δ1的取值范围满足：δ1至少不小于3.0mm；且/或，风轮18与后蜗舌1113的间距δ2的取值范围满足：δ2至少不小于3.0mm。以使该δ1和δ2不至于过小而影响安装。
本申请实施例中，空调室内机100的横截面上，风轮18的中心至前蜗舌1353最近点的连线与风轮18的中心至后蜗舌1113最近点的连线所形成的夹角为出风圆弧角β，β至少不小于160°且不超过185°。
可选地，参见图3，定义第二辅助直线，第二辅助直线经O点，并朝向垂直于后蜗舌1113方向延伸，与后蜗舌1113交汇于N点；定义第三辅助直线，第三辅助直线经O点，并朝向垂直于前蜗舌1353方向，与前蜗舌1353交汇于M点，∠NOM=β。
结合图12至图15，本申请给出方案C和方案D，用以测试间距δ1和δ2对风轮18效率及噪声的影响程度。被测空调室内机100的基本信息：贯流风轮18的外径D2=98mm，贯流风轮18的长度630mm，该贯流风轮18的长度与空调器的长度方向一致，蒸发器17为两排7mm管径开窗片、胀管高度635mm，壁挂机的机壳10尺寸：830mm×300mm×205mm，风机出风圆弧角β不超过170°，根据以上各参数，若需要满足δ1至少不小于0.035D2且不超过0.065D2、δ2至少不小于0.035D2且不超过0.065D2，则需要δ1和δ2的取值在3.43mm~6.37mm范围内。
方案C中，风轮18与前蜗舌1353的间距δ1 =4.8mm，风轮18与后蜗舌1113的间距δ2=4.5mm，方案C中，δ1和δ2的取值均位于0.035D2至0.065D2范围内。
方案D中，风轮18与前蜗舌1353的间距δ1 =6.5mm，风轮18与后蜗舌1113的间距δ2=6.2mm；方案D中，δ1和δ2的取值均大于0.035D2至0.065D2范围。
图12所示为，为方案C和方案D中风轮18的转速分别在900rpm、1000rpm、1100rpm和1200rpm所对应的风量、功率和噪声值，根据图12中图表的数据结果，分别给出了图13所示的风量曲线示意图、图14所示的功率曲线示意图和图15所示的噪声曲线示意图，能更直观的体现方案A和方案B中风量、功率和噪声值之间的关系。结合图13至图15，方案D较方案C，同转速下风量约损失6.5%-7.5%，同风量下功率也略高，约2%-3%，同风量下噪声高0.6-1.0dBA，风机送风效率降低，同时噪声也恶化。方案C中，δ1和δ2落在优选区间内，方案D中，δ1和δ2偏大，未落在优选区间内，由此可知，空调室内机100满足δ1至少不小于0.035D2且不超过0.065D2，δ2至少不小于0.035D2且不超过0.065D2时，同转速下风轮18的送风量增大、送风效率提高，同时噪声减小。
本申请技术方案中，机壳10包括底盘11、面框13和前面板15，前面板15连接于面框13的前侧，底盘11连接于面框13的后侧，底盘11的下端形成为风道下壁111，面框13的下端形成为风道上壁135，进风口131位于面框13的顶部，出风口133位于面框13的下部。
空调室内机100的风道内还设有滤网等结构，空气由进风口131进入风道内，先经过滤网过滤后，再与蒸发器17进行换热，机壳10上于进风口131处还安装有进风格栅，该进风格栅能防止体积较大的物体误入风道内，以对风道内的结构进行初步保护，过滤网则能进一步对风道内的结构进行保护，而且能对空气进行过滤，以使得出风口133处送出的空气更加洁净，质量更好。
风道内还可以增设有电辅热，当空调器进行制热过程时，该电辅热能够进一步提高空调器的制热效率。
进一步地，蒸发器17包括位于风轮18与前面板15之间的前蒸段171，前蒸段171与前面板15的间距为L4，L4至少不小于0.2D2。
该实施例中，将前蒸段171与前面板15的间距限定为大于或等于0.2D2，使得前蒸段171前方留有足够空间，使前蒸段171处空气流量增大，进一步改善蒸发器17整体速度分布均匀性，改善喘振、提升换热效率。若该前蒸段171与前面板15的间距L4的取值小于0.2D2则会使得前蒸段171与前面板15之间的间隙过小，造成前蒸段171处换热效果不佳。
本申请还提出一种空调器，该空调器包括空调室外机和空调室内机100，该空调室内机100的结构参照上述实施例，由于本空调器采用了上述所有实施例的全部技术方案，因此至少具有上述实施例的技术方案所带来的所有效果，在此不再一一赘述。
以上所述仅为本申请的优选实施例，并非因此限制本申请的专利范围，凡是在本申请的申请构思下，利用本申请说明书及附图内容所作的等效结构变换，或直接/间接运用在其他相关的技术领域均包括在本申请的专利保护范围内。

Claims (19)

  1. 一种空调室内机，其中，包括机壳，所述机壳开设有进风口和出风口，且形成有连通所述进风口和出风口的风道，所述风道内设有风轮，以及围设于风轮外侧的蒸发器；
    所述风轮于水平面的投影于前后方向上落入所述进风口于水平面的投影范围内；
    且，所述进风口在水平面的投影于前后方向上的长度为Lin，所述风轮的外径为D2，Lin至少不小于1.5D2。
  2. 如权利要求1所述的空调室内机，其中，所述风轮的前侧于水平面的投影与所述进风口的前侧于水平面的投影距离大于0.5D2。
  3. 如权利要求1所述的空调室内机，其中，所述机壳包括风道上壁和风道下壁，所述风道上壁和风道下壁之间形成出风风道；
    所述风道上壁包括上壁连接段和前蜗舌，所述前蜗舌自所述上壁连接段靠近所述进风口的一端折弯形成，所述前蜗舌朝向所述进风口延伸；
    所述风道下壁包括下壁连接段和后蜗舌，所述后蜗舌自所述下壁连接段靠近所述进风口的一端朝向所述进风口延伸设置。
  4. 如权利要求3所述的空调室内机，其中，所述风道上壁和风道下壁的最小间距为Lout，Lout至少是0.42D2且不超过 0.57D2。
  5. 如权利要求3所述的空调室内机，其中，所述上壁连接段和所述下壁连接段相对设置，且所述上壁连接段和所述下壁连接段沿背离出风方向延伸的延长线相交形成扩压角θ，所述扩压角θ的取值范围为：θ至少大于过0°且不超过180°。
  6. 如权利要求5所述的空调室内机，其中，所述扩压角θ的取值范围为：θ至少不小于5°且不超过25°。
  7. 如权利要求3所述的空调室内机，其中，所述下壁连接段的长度为L3，L3至少不小于0.15D2。
  8. 如权利要求3所述的空调室内机，其中，所述风轮与所述前蜗舌的间距为δ1，δ1至少不小于0.035D2且不超过0.065D2。
  9. 如权利要求8所述的空调室内机，其中，所述风轮与所述前蜗舌的间距δ1的取值范围为：δ1至少不小于3.0mm。
  10. 如权利要求3所述的空调室内机，其中，所述风轮与所述后蜗舌的间距为δ2，δ2至少不小于0.035D2且不超过0.065D2。
  11. 如权利要求10所述的空调室内机，其中，所述风轮与所述后蜗舌的间距δ2的取值范围为：δ2至少不小于3.0mm。
  12. 如权利要求3所述的空调室内机，其中，所述空调室内机的横截面上，所述风轮的中心至所述前蜗舌最近点的连线与所述风轮的中心至所述后蜗舌最近点的连线所形成的夹角为出风圆弧角β，β至少不小于160°且不超过185°。
  13. 如权利要求3至12中任一所述的空调室内机，其中，所述机壳包括底盘、面框和前面板，所述前面板连接于所述面框的前侧，所述底盘连接于所述面框的后侧，所述底盘的下端形成为所述风道下壁，所述面框的下端形成为所述风道上壁，所述进风口位于所述面框的顶部，所述出风口位于所述面框的下部。
  14. 如权利要求13所述的空调室内机，其中，所述蒸发器包括位于所述风轮与所述前面板之间的前蒸段，所述前蒸段与所述前面板的间距为L4，L4至少不小于0.2D2。
  15. 如权利要求14所述的空调室内机，其中，所述蒸发器还包括中蒸段和后蒸段，所述前蒸段、所述中蒸段及所述后蒸段依次连接，所述中蒸段和所述后蒸段的一端于所述风轮的上方相连接，所述后蒸段背离所述中蒸段的一端朝向所述风轮的后侧方向延伸，所述中蒸段背离所述后蒸段的一端朝向所述风轮的前侧方向延伸。
  16. 如权利要求13所述的空调室内机，其中，所述空调室内机还包括滤网，所述滤网设于所述风道内，并位于所述进风口和所述蒸发器之间。
  17. 如权利要求13所述的空调室内机，其中，所述空调室内机还包括进风格栅，所述机壳于所述进风口处安装有所述进风格栅。
  18. 如权利要求13所述的空调室内机，其中，所述空调室内机还包括电辅热，所述电辅热安装于所述风道内。
  19. 一种空调器，其中，包括空调室外机和如权利要求1至18中任意一项所述的空调室内机。
PCT/CN2019/109140 2018-11-19 2019-09-29 空调室内机和空调器 Ceased WO2020103579A1 (zh)

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CN112303711B (zh) * 2019-07-30 2022-02-25 广东美的制冷设备有限公司 壁挂式空调室内机
CN110736141A (zh) * 2019-11-04 2020-01-31 广东美的暖通设备有限公司 室内机和空调器
CN113028623B (zh) * 2021-04-12 2024-12-03 珠海格力电器股份有限公司 风道挡风结构及具有其的空调器
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