CN103851694B - Indoor unit of air conditioner - Google Patents
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- CN103851694B CN103851694B CN201210501618.7A CN201210501618A CN103851694B CN 103851694 B CN103851694 B CN 103851694B CN 201210501618 A CN201210501618 A CN 201210501618A CN 103851694 B CN103851694 B CN 103851694B
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- 238000004378 air conditioning Methods 0.000 claims description 7
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- 208000037656 Respiratory Sounds Diseases 0.000 description 2
- 206010047924 Wheezing Diseases 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
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- 238000007664 blowing Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
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Abstract
The invention provides an indoor unit of an air conditioner, which comprises a shell, a heat exchanger and a cross-flow fan, wherein the heat exchanger and the cross-flow fan are arranged in the shell; the volute comprises a front volute tongue forming a first side surface of a diffusion part of the cross-flow fan and a rear volute forming a second side surface of the diffusion part opposite to the first side surface, the diffusion part is arranged downwards and forms an air outlet on the lower side surface of the shell, and the rear side surface and/or the upper side surface of the shell are/is provided with an air return opening; the minimum clearance between the front volute tongue and the rear volute is D, wherein D is more than or equal to 40mm and less than or equal to 75 mm. According to the invention, the air outlet is arranged on the lower side surface, and the air return inlet is arranged on the rear side surface and/or the upper side surface, so that local ceiling of a room is realized, and the air flow circulation of the whole room is improved. In addition, the invention optimizes the minimum clearance D between the front volute tongue and the rear volute and adjusts the size of the air outlet, thereby optimizing the air outlet speed and reducing the noise.
Description
Technical Field
The invention relates to the field of air conditioners, in particular to an indoor unit of an air conditioner.
Background
With the improvement of living standard of people, people pay more and more attention to the decoration of rooms, and the hidden room air conditioning unit is gradually popular to people due to the advantage of concealment. The air inlet and outlet forms of the hidden air-conditioning indoor unit with one-way air outlet in the current market mainly comprise two forms, the first form is a hidden air-conditioning indoor unit with a lower inlet and a side outlet, namely, an air return opening 11 is arranged on the lower bottom surface of the air-conditioning indoor unit, and an air outlet 12 is arranged on the rear side surface of the air-conditioning indoor unit. Fig. 1 is a schematic view of a cross section of an air flow after an indoor unit of a bottom-in side-out type concealed air conditioner is installed, the concealed air conditioner indoor unit of the bottom-in side-out type has the advantages that only a local ceiling of a room is needed by adopting the bottom-in side-out type, and a large amount of ceiling space of the room is saved, but as shown in fig. 1, air outlet of the indoor unit of the air conditioner firstly reaches the top of the room and then circulates downwards through the air flow, and a human activity area is in the middle lower part of the room, so that a large waste; and when the air conditioner heats, because the density of the hot air is lower, the hot air is difficult to reach the lower part in the room, and the thermal comfort is poor.
In the other type, the lower inlet and lower outlet hidden indoor unit of air conditioner has air return port 11 and air outlet port 12 on the lower side of the indoor unit. Fig. 2 is a schematic cross-sectional view of airflow after installation of a bottom-in and bottom-out concealed indoor air conditioner, wherein the bottom-in and bottom-out concealed indoor air conditioner is installed in a manner that the outlet air of the indoor air conditioner is easier to be delivered to the middle lower part of a room. However, the airflow circulation area of the lower-inlet and lower-outlet type air conditioner indoor unit is small and needs to be installed in the middle area of a room, so that the whole ceiling is needed for the room, the height of the room is reduced, and the oppressive feeling is easily caused. Moreover, the air outlet 12 and the air return opening 11 are close to each other, so that the air flow is difficult to reach the corner of the room, the temperature difference of the room is large, and the comfort is not good.
Disclosure of Invention
The invention aims to provide an indoor unit of an air conditioner, which solves the problem that the existing hidden indoor unit of the air conditioner cannot simultaneously meet the requirements of a local ceiling and good heating comfort of the indoor middle-lower part.
The invention provides an indoor unit of an air conditioner, which comprises a shell, a heat exchanger and a cross-flow fan, wherein the heat exchanger and the cross-flow fan are arranged in the shell; the volute comprises a front volute tongue forming a first side surface of a diffusion part of the cross-flow fan and a rear volute forming a second side surface of the diffusion part opposite to the first side surface, the diffusion part is arranged downwards and forms an air outlet on the lower side surface of the shell, and the rear side surface and/or the upper side surface of the shell are/is provided with an air return opening; the minimum clearance between the front volute tongue and the rear volute is D, wherein D is more than or equal to 40mm and less than or equal to 75 mm.
Further, D is more than or equal to 45mm and less than or equal to 65 mm.
Furthermore, an included angle between the front volute tongue and the rear volute is opened towards the air outlet side to form a diffusion angle gamma of the diffusion part, wherein the gamma is more than or equal to 10 degrees and less than or equal to 40 degrees.
Further, the minimum gap between the edge of the cross-flow wind wheel and the front volute tongue is 1, wherein 3mm is less than or equal to 1 and less than or equal to 13 mm; the minimum clearance of the volute is 2 after the edge of the through-flow wind wheel is away from the volute, wherein 3mm is less than or equal to 2mm and less than or equal to 15 mm.
Further, the air inlet angle of the cross-flow fan is alpha, wherein alpha is more than or equal to 120 degrees and less than or equal to 250 degrees; the air outlet angle of the cross-flow fan is beta, wherein beta is more than or equal to 110 degrees and less than or equal to 240 degrees, and alpha + beta is less than or equal to 360 degrees.
Further, the heat exchanger is a double-fold heat exchanger, the double-fold heat exchanger comprises a first heat exchanging part and a second heat exchanging part which are connected with each other, an included angle theta 1 is formed between the first heat exchanging part and the second heat exchanging part, and the theta 1 is larger than or equal to 20 degrees and smaller than or equal to 150 degrees.
Further, the heat exchanger is a multi-fold heat exchanger which is more than two-fold.
Furthermore, an included angle is formed between the second side surface of the diffusion part and the lower side surface of the shellWherein,
furthermore, the included angle between the connecting line of the closest point of the rear volute and the cross-flow wind wheel and the circle center of the cross-flow wind wheel and the horizontal line is omega, wherein omega is more than or equal to 40 degrees and less than or equal to 120 degrees.
Furthermore, the vertical distance from the circle center of the cross-flow wind wheel to the air outlet on the lower side surface of the shell is L, wherein L is more than or equal to 60mm and less than or equal to 180 mm.
According to the air conditioner indoor unit, the air outlet is arranged on the lower side surface, and the air return opening is arranged on the rear side surface and/or the upper side surface, so that local ceiling of a room is realized, a large amount of ceiling space of the room is saved, air flow can be easily sent to the middle lower part of the room, air flow circulation of the whole room is improved, and comfort is improved. In addition, the invention optimizes the minimum clearance D between the front volute tongue and the rear volute and adjusts the size of the air outlet, thereby optimizing the air outlet speed, ensuring the air outlet speed to be more stable and reducing the noise.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
FIG. 1 is a schematic view of the air circulation of a bottom-return side-out type indoor unit of an air conditioner in the prior art;
FIG. 2 is a schematic view of the airflow circulation of a prior art bottom-out air conditioning indoor unit;
fig. 3 is a schematic view showing a side-back bottom-out type air flow circulation of the indoor unit of the air conditioner of the present invention;
fig. 4 is a schematic perspective view of an indoor unit of an air conditioner according to the present invention;
fig. 5 is a schematic sectional view of an indoor unit of an air conditioner according to the present invention, along a radial direction of a cross flow wind wheel;
fig. 6 is a schematic view showing the interrelationship between the components of the indoor unit of an air conditioner according to the present invention;
FIG. 7 is a schematic structural diagram of a heat exchanger of an indoor unit of an air duct according to the present invention, which is a single-fold heat exchanger;
fig. 8 is a schematic view of a first structure of a heat exchanger of an indoor unit of an air duct, which is a multi-fold heat exchanger according to the present invention;
fig. 9 is a second structural schematic diagram of the heat exchanger of the air pipe indoor unit according to the invention, which is a multi-fold heat exchanger; and
FIG. 10 illustrates the omega, L of the air duct indoor unit according to the present invention,The position relationship is shown schematically.
Detailed Description
The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.
As shown in fig. 3 to 6, the indoor unit of an air conditioner according to the present invention includes a casing 10, and a heat exchanger 20 and a cross flow fan 40 disposed inside the casing, wherein the cross flow fan 40 includes a cross flow wind wheel 41 and a scroll 42 disposed in cooperation with each other; the volute 42 comprises a front volute tongue 42a forming a first side surface of a diffusion part 43 of the cross-flow fan 40 and a rear volute 42b forming a second side surface of the diffusion part 43 opposite to the first side surface, the diffusion part 43 is arranged downwards and forms an air outlet 12 on the lower side surface of the shell 10, and the rear side surface and/or the upper side surface of the shell is provided with an air return opening 11; the minimum clearance between the front volute tongue 42a and the rear volute 42b is D, wherein D is more than or equal to 40mm and less than or equal to 75 mm. According to the invention, the air outlet 12 is arranged on the lower side surface, and the air return opening 11 is arranged on the rear side surface and/or the upper side surface, so that local ceiling of a room is realized, a large amount of ceiling space of the room is saved, and air flow can be easily sent to the middle lower part of the room. When the outlet 12 is on the lower side and the return 11 is on the rear side as shown in fig. 3, the airflow circulation is enhanced as shown by the arrows in fig. 3, thereby enhancing the comfort of the whole room. In addition, the invention optimizes the minimum clearance D between the front volute tongue 42a and the rear volute 42b and adjusts the size of the air outlet 12, thereby optimizing the air outlet speed, ensuring the air outlet speed to be more stable and reducing the noise.
Generally, the minimum gap D between the front volute tongue 42a and the rear volute 42b determines the minimum outlet air size of the diffuser 43 of the cross flow fan 40, and when the minimum gap D is too small, the air volume of the indoor unit of the air conditioner is relatively small, and meanwhile, because the outlet air speed is relatively high, the noise is relatively large, and when the minimum gap D is too large, the outlet air speed is unstable.
Specifically, an air conditioner with the refrigerating capacity of 3.5kw customized by one style is used as a testing machine, the diameter of a fan blade is 108mm, the included angle of a diffusion part is 24 degrees, the gap between a cross-flow wind wheel 41 and a front volute tongue 42a is 1=6mm, the gap between the cross-flow wind wheel 41 and a rear volute 42b is 2=5mm, a double-folded heat exchanger is adopted, the total U number of the double-folded evaporator is 16U, the angle between the double-folded heat exchanger is 48 degrees, the angle is 24 degrees with the horizontal plane, and the following experimental data can be obtained by adjusting the minimum D size of the volute tongue and a bottom shell
Table one: maximum air volume and noise data of indoor unit of air conditioner under different D sizes
It can be seen from table one that, when the minimum gap D is too large, the air outlet of the indoor unit of the air conditioner is unstable, and when the minimum gap D between the front volute tongue 42a and the rear volute 42b is 45mm to 65mm, the indoor unit of the air conditioner can obtain a higher air volume-to-noise ratio, and the phenomenon of unstable air outlet cannot occur.
As shown in fig. 6, the diffuser angle γ of the diffuser 43 of the crossflow blower 40 (i.e., the included angle of the opening between the front volute tongue 42a and the rear volute 42 b) is 10 ° or more and γ or less and 40 ° or less. Regarding the air outlet diffusion angle gamma of the indoor unit of the air conditioner, when the diffusion angle gamma is too small, the air volume of the unit is too small, the air speed is large, the noise of the indoor unit of the air conditioner is too large, when the diffusion angle gamma is too large, namely when the air outlet of the unit is too large, the air outlet speed is too low, the air volume of the unit is reduced to a certain extent, the air speed is low, the whole room is not beneficial to forming effective air circulation, the reasonable diffusion angle setting is beneficial to increasing the air flow, improving the air outlet effect and reducing the noise.
A series of tests show that when the diffusion angle gamma is within the range of 10-40 degrees, the air outlet quantity and the noise of the indoor unit of the air conditioner are satisfactory, and the air quantity-noise ratio is good. An air conditioner with refrigerating capacity of 3.5kw customized by one style is used as a testing machine, the diameter of a fan blade is 108mm, the gap between a cross-flow wind wheel 41 and a front volute tongue is 1=6mm, the gap between the cross-flow wind wheel 41 and a rear volute tongue is 2=5mm, an air inlet angle alpha =184 DEG, an air outlet angle beta =176 DEG, a double-folded heat exchanger is adopted, 6 heat exchange U pipes with the diameter of 5mm and 10 heat exchange U pipes with the diameter of 5mm are respectively adopted, different gamma angles are adopted, and when the air conditioner runs at the highest gear, the air volume and noise test data are as shown in the following table two:
table two: test data of air quantity and noise under different gamma angles
| Gamma (degree) | Air volume (cubic meter per hour) | Noise (decibel) |
| 10 | 607 | 41.8 |
| 18 | 628 | 41.6 |
| 24 | 633 | 41.5 |
| 28 | 641 | 42.1 |
| 40 | 616 | 41.9 |
From the above data, it is clear that, in the process of continuously increasing the diffusion angle γ, the air volume and the noise both show a trend of increasing first and then decreasing, and it can also be obtained that, when the diffusion angle γ is selected from a more preferable range of 18 ° -28 °, the air volume of the indoor unit of the air conditioner is greatly increased, and the air volume-to-noise ratio is also high.
As shown in fig. 6, the minimum gap 1 between the edge of the cross-flow wind wheel 41 and the front volute tongue 42a is 3mm or more and 1 or more and 13mm or less; the distance between the edge of the cross flow wind wheel 41 and the minimum gap 2 of the rear volute 42b is less than or equal to 3mm and less than or equal to 2 and less than or equal to 15 mm. The size of the indoor unit of the air conditioner can be reduced, the air outlet volume of the unit is increased, and the noise of the unit is reduced.
The air conditioner with the refrigerating capacity of 3.5kw customized by one style is used as a testing machine, the diameter of a fan blade is selected to be 108mm, the included angle of a diffusion part is 24 degrees, an air inlet angle alpha =184 degrees, an air outlet angle beta =176 degrees, a three-fold heat exchanger is adopted, heat exchange U pipes with the diameters of 4, 5 and 6 and 5mm are adopted, the heights of 1 and 2 are adjusted, and when the air conditioner runs at the highest gear, the air volume and noise test data are shown in the following table III: (dimension unit millimeter, air volume unit cubic meter per hour, noise unit decibel):
table three: test data of air quantity and noise under different conditions of 1 and 2
| δ1 | δ2 | Unit section size (Fan blade radial) | Air quantity | Noise (F) | Air volume to noise ratio |
| 3 | 3 | 303*195 | 651 | 43.2 | 15.1 |
| 5 | 4 | 304*198 | 648 | 41.3 | 15.7 |
| 6 | 5 | 305*200 | 641 | 40.2 | 15.9 |
| 8 | 9 | 309*211 | 574 | 39.4 | 14.6 |
| 13 | 15 | 315*217 | 482 | 37.2 | 13.0 |
From the above data, it can be seen that when 1 and 2 are too small, although the air volume noise is relatively large, the noise is also relatively large, which is not the most preferable solution, and comparing the above data, it can be seen that when 5mm ≦ 1 ≦ 8mm, 4mm ≦ 2 ≦ 9mm, both the air volume and noise can be in the more preferable range, and the air volume-to-noise ratio also takes on the more preferable value.
As shown in fig. 6, an air inlet angle of the cross-flow fan (an included angle between a connection line of a circle center of the cross-flow wind wheel 41 and a shortest distance point on the rear volute and a connection line of a circle center of the cross-flow wind wheel and a shortest distance point of the front volute tongue) is α, an air outlet angle of the cross-flow fan (an included angle between a connection line of a circle center of the cross-flow wind wheel 41 and a shortest distance point of the bottom casing and a connection line of a circle center of the cross-flow wind wheel and a shortest distance point of the front volute tongue) is β, and the air inlet angle α and the air outlet angle β are generally equal to or greater than; beta is more than or equal to 110 degrees and less than or equal to 240 degrees. The sum of the inlet angle α and the outlet angle β is less than or equal to 360 degrees, and when the boundary between the inlet angle α and the outlet angle β is a point, α + β =360 °, generally, the boundary is a small line segment, so α + β < 360 °.
When the air inlet angle alpha is too small, the air volume of the unit is small, the air volume of the air outlet is unstable, and the unit has wheezing sound. An air conditioner with refrigerating capacity of 3.5kw customized by one style is used as a testing machine, the diameter of a fan blade is selected to be 108mm, the included angle of a diffusion part is 24 degrees, the gap between a cross flow wind wheel 41 and a front volute tongue is 1=6mm, the gap between the cross flow wind wheel 41 and a rear volute is 2=5mm, a double-folded heat exchanger is adopted, namely 6 heat exchange U pipes with the diameter of 5mm and 10 heat exchange U pipes with the diameter of 5mm, different alpha and beta angles are adopted, and when the air conditioner runs at the highest gear, the air volume and noise test data are as shown in the following table four: (size unit millimeter, air volume unit cubic meter per hour)
Table four: test data of air quantity and noise under different alpha and beta
| α | β | Air quantity | Other problems |
| 120 | 240 | 522 | Unstable air outlet volume and wheezing sound |
| 160 | 200 | 587 | |
| 185 | 175 | 634 | |
| 190 | 170 | 628 | |
| 250 | 110 | 541 |
As can be seen from the data in Table four, when the angle alpha is too small, the air quantity is small, the air outlet is unstable, and when the angle beta is too small, the air quantity is small, and the data are contrasted and analyzed, the preferable ranges of the air inlet angle alpha and the air outlet angle beta are that alpha is more than or equal to 160 degrees and less than or equal to 190 degrees, and beta is more than or equal to 170 degrees and less than or equal to 200 degrees.
As shown in fig. 5, a water pan 30 is disposed below the heat exchanger 20, a heat insulating filler 60 is disposed between the water pan 30 and the casing 10, and a heat insulating filler 60 is disposed between the volute 42 and the casing 10. Preferably, the heat insulation filler 60 is sponge or foam, and is used for filling and fixing the water pan or the volute, and simultaneously plays a role in heat preservation and preventing condensation.
As shown in fig. 5 and 6, the heat exchanger 20 can be folded twice, and the heat exchanger can effectively reduce the three-dimensional size of the unit by selecting the heat exchanger with two folds according to the height and the depth of the currently common suspended ceiling, wherein the included angle between the heat exchanger with two folds is theta 1, and theta 1 is more than or equal to 20 degrees and less than or equal to 150 degrees. In consideration of improving the processing efficiency and the structural strength of the heat exchanger, the heat exchanger can adopt an integrated bending form instead of a two-fold splicing form, and meanwhile, the volume of the air conditioner indoor unit can be reduced.
Adopt foretell testing machine, install two and roll over the heat exchanger, the angle between the two heat exchangers of adjustment obtains the experimental data as shown in following table five:
table five: experimental data at different theta 1 angles
It can be seen from table five that when the angle θ 1 is too small, a series of problems such as unsmooth drainage of the heat exchanger, too small air return opening, small air volume of the unit and the like can be caused, and the preferable range of the value of θ 1 is 35 ° to 100 °.
As shown in fig. 7, the heat exchanger 20 may also be a single-fold heat exchanger, which is disposed obliquely to the horizontal plane. As shown in fig. 8 and 9, the heat exchanger 20 may also be a multi-fold heat exchanger with more than two folds, and an included angle θ 2 between any two adjacent folds of the multi-fold heat exchanger is 0 ° or more and 180 ° or less, and preferably 1 ° or more and 179 ° or less, so as to form a half-enclosed structure for the fan, so that the heat exchanger is more uniformly exposed to the wind, and the heat exchange efficiency is improved. When the heat exchanger is arranged more than two folds, the heat exchanger can be designed into 6 folds at most in consideration of maximum efficiency and space utilization by combining the prior art. In the above various heat exchanger arrangement forms, in order to ensure the heat exchange capability of the unit, the sum of the number of U tubes on the cross section of each heat exchanger is 12-24, preferably 13-18.
As shown in fig. 8 to 10, the rear scroll 42b or its tangential surface may be disposed vertically or obliquely to the lower side surface of the housing. As shown in FIG. 10, the second side of the diffuser 43 is angled from the lower side of the housingI.e. the angle between the rear volute 42b or its tangent plane and the lower side of the housing isGenerally, when the unit is designed to have the air outlet area and the air return area in the same area,the angle is acute, when the air return area and the air supply area of the unit are in different areas,at an obtuse angle. More preferably in the range of 30 ° to 170 °. With the testing machine, when the hoisting height is 2.5 m, and the highest wind volume is 634 cubic meters per hour, the angle is adjustedThe experimental results shown in table six below were obtained.
From the experimental results of the sixth table below, it can be seen that the angle is not too largeWhen the air conditioner is too small, a backflow phenomenon exists, and the performance of the air conditioner is influenced. And whenToo small or in transition, i.e. in the table aboveOrIn the process, the lowest air supply height is raised, namely the height from the lowest point which can be reached by wind to the ground is continuously increased, so that the air blowing effect is influenced. The lowest air supply height is less than 0.2mm as an index and the angle isThe most preferred range is 50 ° to 150 °.
Table six: is differentBlowing condition under angle
As shown in fig. 10, the closest point of the rear volute 42b from the cross flow wind wheel 41 is a dividing point between the inlet air and the outlet airFirstly, an angle omega formed by a connecting line between a point on the rear volute 42b closest to the cross-flow wind wheel 41 and the center of the cross-flow wind wheel 41 and the horizontal line controls the proportion of an air inlet area and an air outlet area, when omega is larger, the air inlet area is smaller, the unit air volume is small, the air outlet is unstable, when omega is smaller, the air outlet area is too small, the unit air volume is small, and the value range of omega is generally 40-120 degrees.
An air conditioner with refrigerating capacity of 3.5kw customized by one style is used as a testing machine, the diameter of a fan blade of the air conditioner is 108mm, the gap between a diffusion part included angle 24 DEG cross-flow wind wheel 41 and a front volute tongue is 1=6mm, the gap between the cross-flow wind wheel 41 and a rear volute is 2=5mm, a double-folded heat exchanger is adopted, namely 6 heat exchange U pipes with the diameter of 5mm and 10 heat exchange U pipes with the diameter of 5mm respectively, different omega angles are adopted, and when the air conditioner runs at the highest gear, the test data of the air quantity is as shown in the following seven: (Angle unit degree, air volume unit cubic meter per hour)
TABLE VII: experimental data of air quantity under different omega angles
| ω | Highest wind rate of unit |
| 40 | 546 |
| 60 | 582 |
| 80 | 628 |
| 100 | 623 |
| 120 | 575 |
From the data in the seventh table, it can be seen that, in the process of increasing ω from 40 ° to 120 °, the highest wind rate of the unit increases first and then decreases, and when ω is from 60 ° to 100 °, the wind rate has a better value.
As shown in fig. 10, the distance L from the center of the cross-flow wind wheel 41 to the lowermost end of the air outlet 12 directly controls the diffusion length of the unit, when the diffusion length is too short, stable air outlet cannot be formed, the air outlet volume is low, and the air outlet volume easily enters the stall area of the cross-flow wind wheel 41, when the diffusion length is too long, the diffusion pressure loss is too large, the unit air volume is low, and the value range of general L is as follows: l is more than or equal to 60mm and less than or equal to 180 mm.
An air conditioner with refrigerating capacity of 3.5kw customized by one style is used as a testing machine, a fan blade with the diameter of 98mm, a diffusion part included angle of 24 degrees, an air inlet angle alpha =184 degrees, an air outlet angle beta =176 degrees, a cross-flow wind wheel 41 and a front volute tongue gap of 1=6mm, a cross-flow wind wheel 41 and a rear volute gap of 2=5mm are selected, a double-folded heat exchanger is adopted, namely 6 heat exchange U pipes with the diameter of 5mm and 10 heat exchange U pipes with the diameter of 5mm are respectively adopted, different L are adopted, and when the air conditioner runs at the highest gear, the test data of the air volume are shown in the following table eight: (Length unit is millimeter, air volume unit is cubic meter per hour)
Table eight: experimental data of air volume under different L
| L | Air quantity | Remarks for note |
| 60 | 410 | Unstable air outlet volume |
| 98 | 594 | |
| 120 | 617 | |
| 140 | 573 | |
| 180 | 445 |
The data of the eighth table can be obtained, when L is from the constantly increasing 180 mm's in-process of 60mm, the unit top grade amount of wind reduces after increasing earlier, when L undersize moreover, can lead to the unstable problem of the amount of wind-out. Comprehensively considering, when the L is in the range of 98 mm-140 mm, the air quantity obtains a better value.
Preferably, as shown in fig. 5, an electric heating device 50 is disposed between the heat exchanger 20 and the fan 40, and when the heat exchanger 20 cannot meet the heating requirement, the electric heating device 50 can be activated to compensate for the problem of insufficient power of the heat exchanger 20.
From the above description, it can be seen that the above-described embodiments of the present invention achieve the following technical effects:
according to the air conditioner indoor unit, the air outlet is arranged on the lower side surface, and the air return opening is arranged on the rear side surface and/or the upper side surface, so that local ceiling of a room is realized, a large amount of ceiling space of the room is saved, air flow can be easily sent to the middle lower part of the room, air flow circulation of the whole room is improved, and comfort is improved. In addition, the invention optimizes the minimum clearance D between the front volute tongue and the rear volute and adjusts the size of the air outlet, thereby optimizing the air outlet speed, ensuring the air outlet speed to be more stable and reducing the noise.
The above is only a preferred embodiment of the present invention, and is not intended to limit the present invention, and various modifications and changes will occur to those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (10)
1. An air-conditioning indoor unit, comprising a casing (10), and a heat exchanger (20) and a cross-flow fan (40) arranged inside the casing, characterized in that,
the cross-flow fan (40) comprises a cross-flow wind wheel (41) and a volute (42) which are matched with each other;
the volute (42) comprises a front volute tongue (42 a) forming a first side surface of a diffuser (43) of the cross-flow fan (40) and a rear volute (42 b) forming a second side surface, opposite to the first side surface, of the diffuser (43), the diffuser (43) is arranged downwards, an air outlet (12) is formed in the lower side surface of the shell (10), and an air return opening (11) is formed in the rear side surface and/or the upper side surface of the shell;
the minimum clearance between the front volute tongue (42 a) and the rear volute (42 b) is D, wherein D is more than or equal to 40mm and less than or equal to 75 mm.
2. An indoor unit of an air conditioner according to claim 1, wherein D is 45mm or more and 65mm or less.
3. An indoor unit of an air conditioner according to claim 1,
an included angle between the front volute tongue (42 a) and the rear volute (42 b) is opened towards the air outlet side to form a diffusion angle gamma of the diffusion part (43), wherein the gamma is more than or equal to 10 degrees and less than or equal to 40 degrees.
4. An indoor unit of an air conditioner according to claim 1,
the minimum gap between the edge of the cross flow wind wheel (41) and the front volute tongue (42 a) is 1, wherein 3mm is less than or equal to 1 and less than or equal to 13 mm;
the minimum clearance between the edge of the cross flow wind wheel (41) and the rear volute (42 b) is 2, wherein 3mm is less than or equal to 2mm and less than or equal to 15 mm.
5. An indoor unit of an air conditioner according to claim 1,
the air inlet angle of the cross-flow fan (40) is alpha, wherein alpha is more than or equal to 120 degrees and less than or equal to 250 degrees;
the air outlet angle of the cross flow fan (40) is beta, wherein beta is more than or equal to 110 degrees and less than or equal to 240 degrees, and alpha + beta is less than or equal to 360 degrees.
6. An indoor unit of an air conditioner according to claim 1,
the heat exchanger (20) is a double-fold heat exchanger, the double-fold heat exchanger comprises a first heat exchange part and a second heat exchange part which are connected with each other, an included angle theta 1 is formed between the first heat exchange part and the second heat exchange part, and theta 1 is larger than or equal to 20 degrees and smaller than or equal to 150 degrees.
7. The indoor unit of claim 1, wherein the heat exchanger (20) is a multi-fold heat exchanger having more than two folds.
8. Indoor unit of air conditioner according to claim 1, characterized in that the second side of the diffuser (43) is angled with respect to the lower side of the casingWherein,
9. the indoor unit of air conditioner as claimed in claim 1, wherein the angle between the line connecting the nearest point of the rear volute (42 b) to the cross-flow wind wheel (41) and the center of the cross-flow wind wheel (41) and the horizontal line is ω, wherein ω is not less than 40 ° and not more than 120 °.
10. An indoor unit of an air conditioner according to claim 1,
the vertical distance from the circle center of the cross-flow wind wheel (41) to the air outlet (12) on the lower side surface of the shell (10) is L, wherein L is more than or equal to 60mm and less than or equal to 180 mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210501618.7A CN103851694B (en) | 2012-11-28 | 2012-11-28 | Indoor unit of air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210501618.7A CN103851694B (en) | 2012-11-28 | 2012-11-28 | Indoor unit of air conditioner |
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| Publication Number | Publication Date |
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| CN103851694A CN103851694A (en) | 2014-06-11 |
| CN103851694B true CN103851694B (en) | 2016-12-21 |
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| CN201210501618.7A Active CN103851694B (en) | 2012-11-28 | 2012-11-28 | Indoor unit of air conditioner |
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Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104061668B (en) * | 2014-06-17 | 2016-11-09 | 珠海格力电器股份有限公司 | Indoor unit of air conditioner |
| CN104154638B (en) * | 2014-08-18 | 2018-03-27 | 广东美的暖通设备有限公司 | Embedded air-conditioner indoor set |
| CN109282466B (en) * | 2018-09-04 | 2024-04-16 | 奥克斯空调股份有限公司 | Air duct assembly and air conditioner |
| CN109000349B (en) * | 2018-09-04 | 2023-08-15 | 奥克斯空调股份有限公司 | Air duct assembly and air conditioner |
| CN109000351B (en) * | 2018-09-04 | 2023-07-18 | 奥克斯空调股份有限公司 | Air duct assembly and air conditioner |
| CN108844209B (en) * | 2018-09-04 | 2023-07-18 | 奥克斯空调股份有限公司 | Air duct assembly and air conditioner |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3898411B2 (en) * | 2000-03-14 | 2007-03-28 | 三菱電機株式会社 | Cross-flow fan design method and air conditioner |
| JP3564414B2 (en) * | 2001-03-23 | 2004-09-08 | 三菱重工業株式会社 | Indoor unit and air conditioner |
| KR20080044039A (en) * | 2006-11-15 | 2008-05-20 | 삼성전자주식회사 | A ceiling type air conditioner |
| CN201982367U (en) * | 2011-04-15 | 2011-09-21 | 珠海格力电器股份有限公司 | Cross-flow fan and air conditioner with same |
| CN102644975A (en) * | 2012-05-18 | 2012-08-22 | 珠海格力电器股份有限公司 | Indoor unit of air conditioner |
| CN202947215U (en) * | 2012-11-28 | 2013-05-22 | 珠海格力电器股份有限公司 | Indoor unit of air conditioner |
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