CN103486661B - Air pipe indoor unit - Google Patents
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- CN103486661B CN103486661B CN201210194813.XA CN201210194813A CN103486661B CN 103486661 B CN103486661 B CN 103486661B CN 201210194813 A CN201210194813 A CN 201210194813A CN 103486661 B CN103486661 B CN 103486661B
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- Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
Abstract
The invention provides an air pipe indoor unit which comprises a shell, wherein a heat exchanger is fixedly arranged in the shell, a fan is arranged on one side of the heat exchanger, an air return port and an air outlet which are respectively positioned on two sides of the heat exchanger are arranged on the shell, and the air outlet is arranged on the lower side surface of the shell. According to the air pipe indoor unit, the air outlet is arranged on the lower side surface of the shell, so that the air outlet direction of the air pipe indoor unit is directly downward, the problem that the air outlet direction of a common air pipe indoor unit can be downward only by installing the air pipe is effectively solved, and the air outlet efficiency and the heating comfort are improved.
Description
Technical field
The present invention relates to air-cooled ducted air conditioner field, in particular to a kind of air pipe indoor machine.
Background technology
Household small-size air pipe indoor machine the most on the market is for set structure, as shown in Figures 1 to 4, mainly include housing 10, housing 10 is internal is fixedly installed heat exchanger 20, the lower section of heat exchanger 20 is provided with drip tray 30, the side of heat exchanger 20 is provided with blower fan 40, and housing 10 is provided with return air inlet 11 and the air outlet 12 being positioned at heat exchanger 20 both sides.For the mode of air current composition, mainly there is following several form:
Side is sent next time, as depicted in figs. 1 and 2, the return air inlet 11 of air pipe indoor machine designs in indoor set unit bottom, and the air outlet 12 of air pipe indoor machine designs in indoor set unit side, return air, air-out all can air duct or be flexible coupling, form side and send air current composition loop next time.
Side is returned after sending, or side is sent next time, as shown in Figure 3 and Figure 4, the return air inlet 11 of air pipe indoor machine designs at indoor set unit rear portion, the air outlet 12 of air pipe indoor machine designs in indoor set unit side, return air by airduct be connected to unit rear portion, air-out can air duct or be flexible coupling, form the air current composition loop gone back to after side is sent, or air-out can air duct or be flexible coupling be turned downwards, form side and send form next time.
Can be seen that from above air pipe indoor machine structure, air current composition mode, although the household small-size air pipe indoor machine structure of industry is various informative at present, but for reality is installed and used, form is single, the air outlet 12 of unit is all disposed within the side of housing, and during actually used, it is typically necessary air-out direction downward, thus need to install airduct, cause installation trouble, it is additionally, since the existence of airduct, causes that to heat comfortableness poor.
Summary of the invention
It is desirable to provide the air pipe indoor machine of a kind of downward air-out, to solve the problem that the air-out of air pipe indoor machine side heats comfortableness difference.
The invention provides a kind of air pipe indoor machine, including housing, enclosure interior is fixedly installed heat exchanger, and the side of heat exchanger is provided with blower fan, and housing is provided with return air inlet and the air outlet laying respectively at heat exchanger both sides, and air outlet is arranged on the downside of housing.
Further, heat exchanger is arranged on the inlet side of blower fan, and the diffusion portion of blower fan is down-set.
Further, blower fan is cross flow fan, and the tubular wine wheel and spiral case arranged including cooperating, spiral case is equipped with in enclosure interior；Spiral case includes the front spiral case forming the first side, diffusion portion and forms the rear spiral case of the second side, diffusion portion.
Further, the angle between front spiral case and rear spiral case opens to air side, forms the diffusion angle γ in diffusion portion, wherein, 10 °≤γ≤40 °.
Further, 18 °≤γ≤28 °.
Further, before the Edge Distance of tubular wine wheel, the minimum clearance of spiral case is δ 1, wherein 3mm≤δ 1≤13mm；After the Edge Distance of tubular wine wheel, the minimum clearance of spiral case is δ 2, wherein 3mm≤δ 2≤15mm.
Further, 5mm≤δ 1≤8mm；4mm≤δ2≤9mm.
Further, the flow inlet angle of cross flow fan is α, wherein, and 120 °≤α≤250 °；The efflux angles of cross flow fan is β, wherein, and 110 °≤β≤240 °, and alpha+beta≤360 °.
Further, 160 °≤α≤190 °；140°≤β≤200°.
Further, the lower section of heat exchanger is provided with drip tray, is provided with thermal insulating filler between drip tray and housing；Thermal insulating filler it is provided with between spiral case and housing.
Further, heat exchanger is single folding heat exchanger.
Further, heat exchanger is two folding heat exchangers, and two folding heat exchangers include interconnective first heat exchanging part and the second heat exchanging part, has angle theta 1, wherein, 20 °≤θ 1≤150 ° between the first heat exchanging part and the second heat exchanging part.
Further, 35 °≤θ 1≤100 °.
Further, two folding heat exchanger one bending formings, or by two separate exchangers spicing forming types.
Further, heat exchanger is the many foldings heat exchanger more than two foldings.
Further, many folding heat exchanger one bending formings, or by multiple separate exchangers spicing forming types.
Further, between two discharging the retained water of the arbitrary neighborhood of many folding heat exchangers, there is angle theta 2, wherein, 0 °≤θ 2≤180 °.
Further, in included angle between outer contour and the downside of housing in diffusion portion, wherein, 30 °≤φ≤170 °.
Further, 50 °≤φ≤150 °.
Further, the rear spiral case line from the center of circle of closest approach and the tubular wine wheel of tubular wine wheel is ω with horizontal angle, wherein, and 40 °≤ω≤120 °.
Further, 60 °≤ω≤100 °.
Further, the vertical distance of air outlet on the center of circle of tubular wine wheel to the downside of housing is L, wherein, and 60mm≤L≤180mm.
Further, 98mm≤L≤140mm.
Further, return air inlet includes the rear return air inlet being arranged on housing trailing flank and the upper return air inlet of the upper side being arranged on housing；Air pipe indoor machine also includes the return air cover plate being arranged on housing, and return air cover plate has and covers return air inlet and make air pipe indoor machine from the primary importance of rear return air inlet return air；Make air pipe indoor machine from the second position of upper return air inlet return air with covering rear return air inlet；And open the 3rd position making air pipe indoor machine from upper return air inlet and rear return air inlet return air simultaneously.
Further, electric heater unit it is provided with between heat exchanger and blower fan.
Air pipe indoor machine according to the present invention, air outlet is arranged on the downside of housing, so that the air-out direction of air pipe indoor machine is directly down, efficiently solve common air pipe indoor machine to need that airduct is installed and just can make the downward problem of air-out direction, and improve air-out efficiency and the comfortableness heated.
Accompanying drawing explanation
The accompanying drawing of the part constituting the application is used for providing a further understanding of the present invention, and the schematic description and description of the present invention is used for explaining the present invention, is not intended that inappropriate limitation of the present invention.In the accompanying drawings:
Fig. 1 is the first structural representation of the air pipe indoor machine according to prior art；
Fig. 2 is the second structural representation of the air pipe indoor machine according to prior art；
Fig. 3 is the third structural representation of the air pipe indoor machine according to prior art；
Fig. 4 is the 4th kind of structural representation of the air pipe indoor machine according to prior art；
Fig. 5 is the perspective view of the air pipe indoor machine according to the present invention；
Fig. 6 is the sectional structure schematic diagram of the air pipe indoor machine according to the present invention；
Fig. 7 is the mutual relation schematic diagram between each parts of the air pipe indoor machine according to the present invention；
Fig. 8 be the heat exchanger of the air pipe indoor machine according to the present invention be single structural representation rolling over heat exchanger；
Fig. 9 is the first structural representations rolling over heat exchanger the heat exchanger of the air pipe indoor machine according to the present invention is more；
Figure 10 is the second structural representations rolling over heat exchanger the heat exchanger of the air pipe indoor machine according to the present invention is more；
Figure 11 is ω, L, φ position relationship schematic diagram of the air pipe indoor machine according to the present invention；And
Figure 12 is the schematic diagram that the return air cover plate of the air pipe indoor machine according to the present invention is positioned at the 3rd position.
Detailed description of the invention
Describe the present invention below with reference to the accompanying drawings and in conjunction with the embodiments in detail.
As illustrated in Figures 5 and 6, air pipe indoor machine according to the present invention, including housing 10, housing 10 is internal is fixedly installed heat exchanger 20, the lower section of heat exchanger 20 is provided with drip tray 30, the side of heat exchanger 20 is provided with blower fan 40, and housing 10 is provided with return air inlet 11 and the air outlet 12 laying respectively at heat exchanger 20 both sides, and air outlet 12 is arranged on the downside of housing 10.Air outlet 12 is arranged on the downside of housing, so that the air-out direction of air pipe indoor machine is directly down, efficiently solve common air pipe indoor machine to need that airduct is installed and just can make the downward problem of air-out direction, and improve air-out efficiency and the comfortableness heated.
As shown in Figure 6, heat exchanger 20 is arranged on the inlet side of blower fan 40, and the diffusion portion 43 of blower fan 40 is down-set, so, blows out downwards from the air outlet 12 of air pipe indoor machine directly down from the wind of blower fan 40 blowout, need not change wind direction, improve the efficiency of blower fan.
Preferably, blower fan 40 is cross flow fan, including cooperate arrange tubular wine wheel 41 and spiral case 42, spiral case 42 is equipped with inside housing 10, and spiral case 42 Open Side Down arrange, i.e. the diffusion portion of cross flow fan is down-set.Spiral case 42 includes front spiral case 42a and rear spiral case 42b, forms down-set diffusion portion 43 between front spiral case 42a and rear spiral case 42b, so that from the air-flow of air outlet blowout directly down.It is highly preferred that the diffusion angle γ in diffusion portion 43 (angle of the opening between the most front spiral case 42a and rear spiral case 42b) is 10 °≤γ≤40 °.For the air-out diffusion angle γ of indoor apparatus of air conditioner, when diffusion angle γ design is too small, unit air quantity is the least, wind speed is bigger, cause noise of indoor unit of air conditioner excessive, when diffusion angle γ design is the biggest, when i.e. the air outlet of unit is the biggest, go out wind velocity the lowest, the air quantity of unit reduces the most to a certain extent, and rational diffusion angle is arranged, and contributes to increasing air mass flow, improve air-out effect, reduce noise.
Being found by a series of test, when diffusion angle γ is the scope of 10 °～40 °, air output and the noise of indoor apparatus of air conditioner are the most satisfied, have preferable air quantity noise ratio.Air-conditioner using a specified refrigerating capacity as 3.5kw is as testing machine, its fan blade diameter 108mm, tubular wine wheel 41 and front spiral case gap delta 1=6mm, tubular wine wheel 41 and rear spiral case gap delta 2=5mm, flow inlet angle α=184 °, give vent to anger angle beta=176 °, use two-fold heat exchanger, be that heat exchange U pipe and 10 diameter 5mm heat exchange U of 6 a diameter of 5mm manage respectively, use different γ angles, when air-conditioner operates in the most high-grade, air quantity and noise test data are as shown in following table one:
Table one: under different γ angles, the test data of air quantity and noise
| γ (spends) | Air quantity (cubic meter is 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 above data it should be apparent that, during diffusion angle γ constantly increases, air quantity and noise all present the trend of first increases and then decreases, can also draw, when diffusion angle γ selects preferred scope 18 °～28 °, the air quantity of indoor apparatus of air conditioner has bigger lifting, and its air quantity noise ratio is the highest.
As it is shown in fig. 7, minimum clearance δ 1 of spiral case 42a, wherein 3mm≤δ 1≤13mm before the Edge Distance of tubular wine wheel 41；Minimum clearance δ 2 of spiral case 42b, wherein 3mm≤δ 2≤15mm after the Edge Distance of tubular wine wheel 41.The size being possible not only to reduce air pipe indoor machine is so set, increases unit air-out volume simultaneously and reduce unit noise.
Air-conditioner using a specified refrigerating capacity as 3.5kw is as testing machine, select fan blade diameter 108mm, diffusion portion angle 24 degree, flow inlet angle α=184 °, give vent to anger angle beta=176 °, use three folding heat exchangers, be 4,5,6 diameter 5mm heat exchange U pipes respectively, regulation δ 1 and δ 2 height, when air-conditioner operates in the most high-grade, shown in air quantity and noise test data such as following table two (dimensional units millimeter, air quantity cubic unit rice per hour, noise unit decibel):
Table two: different δ 1 and δ 2 time, the test data of air quantity and noise
| δ1 | δ2 | Unit sectional dimension (fan blade is radially) | Air quantity | Noise | Air quantity 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 |
Can be seen that from above data, when δ 1 and δ 2 is too small, although air quantity noise ratio, but its noise is the biggest, is not most preferred scheme, contrast data above, it can be seen that as 5mm≤δ 1≤8mm, 4mm≤δ 2≤9mm, air quantity and noise can be in more preferably scopes, and air quantity noise ratio also obtains and is preferably worth.
The flow inlet angle of cross flow fan 40 (on the center of circle of tubular wine wheel 41 and rear spiral case the short distance point center of circle to tubular wine wheel and the angle of front spiral case short distance point) is α, the efflux angles (center of circle of tubular wine wheel 41 and the drain pan short distance point center of circle to tubular wine wheel and the angle at the shortest strong point of front spiral case) of cross flow fan 40 is β, flow inlet angle α and angle beta of giving vent to anger, usually, 120 °≤α≤250 °；110°≤β≤240°.Flow inlet angle α and angle beta sum of giving vent to anger are less than or equal to 360 degree, and when the boundary of flow inlet angle α and angle beta of giving vent to anger is a bit, it is believed that alpha+beta=360 °, usually, boundary is a little line segment, therefore alpha+beta ＜ 360 °.
When flow inlet angle α is too small, unit air quantity is little, and air-out volume is unstable, has whoop, and when unit flow inlet angle is excessive, owing to efflux angles is too small, unit air quantity is low.Air-conditioner using a specified refrigerating capacity as 3.5kw is as testing machine, select fan blade diameter 108mm, diffusion portion angle 24 degree, tubular wine wheel 41 and front spiral case gap delta 1=6mm, tubular wine wheel 41 and rear spiral case gap delta 2=5mm, use two-fold heat exchanger, wind is not 6 diameter 5mm heat exchange U pipes and 10 diameter 5mm heat exchange U pipes, use different α, β angles, when air-conditioner operates in the most high-grade, air quantity and noise test data are such as shown in following table three (dimensional units millimeter, air quantity cubic unit rice is per hour):
Table three: under different α and β, the test data of air quantity and noise
| α | β | Air quantity | Other problems |
| 120 | 240 | 522 | Air-out volume is unstable, has whoop |
| 160 | 200 | 587 | |
| 185 | 175 | 634 | |
| 190 | 170 | 628 | |
| 250 | 110 | 541 |
From the data of table three it can be seen that during when α angle too small, cause air quantity little, and air-out is unstable, and β too small time, also cause air quantity little, relative analysis data above, it can be deduced that, flow inlet angle α with angle beta more preferably scope of giving vent to anger is, 160 °≤α≤190 °, 170 °≤β≤200 °.
The lower section of heat exchanger 20 is provided with drip tray 30, is provided with thermal insulating filler 60, is provided with thermal insulating filler 60 between spiral case 42 and housing 10 between drip tray 30 and housing 10.Preferably, thermal insulating filler 60 is sponge or foam, the while of being used for filling fixing drip tray or spiral case, plays insulation effect simultaneously, prevents condensation.
As shown in Figs. 5 to 7, heat exchanger 20 can be two foldings, according to the most universal ceiling height, the degree of depth, selects the heat exchanger of two foldings can effectively reduce unit three-dimensional dimension, and between upper and lower two folding heat exchangers, angle is θ 1,20 °≤θ 1≤150 °.For improving working (machining) efficiency and the consideration of heat exchanger structure intensity, heat exchanger not use the form of two foldings splicings, and can use the form of one bending, can reduce indoor set volume simultaneously.
Use above-mentioned testing machine, two folding heat exchangers be installed, adjust the angle between both heat exchangers, obtain the experimental data as shown in following table four:
Table four: the experimental data under different θ angles
From table four it can be seen that during when θ angle too small, heat exchanger impeded drainage can be caused, return air inlet is the least, and the little span waiting series of problems, preferably θ of unit air quantity is 35～100 °.
As shown in Figure 8, heat exchanger 20 can also be single folding heat exchanger, and single folding heat exchanger is arranged with horizontal plane.As shown in Figures 9 and 10, heat exchanger 20, it can also be provided that be more than many foldings heat exchanger of two foldings, have 0 °≤θ of angle 2≤180 ° between two discharging the retained water of the arbitrary neighborhoods of many folding heat exchangers, thus blower fan is formed semi-surrounding structure, make heat exchanger evenly wind-engaging, improve heat exchange efficiency.When heat exchanger is arranged more than two foldings, for maximal efficiency and the consideration utilizing space, in conjunction with current existing technique, heat exchanger at most may be designed to 6 foldings.Arranging in form at any of the above heat exchanger, in order to ensure the exchange capability of heat of unit, heat exchanger cross section U pipe number sum is 12～24, preferably 13～18.
As shown in figure 11, in order to make air circulation more rationally and meet different air-supply area requirement, the front spiral case 42a and rear spiral case 42b of both sides, diffusion portion 43 may be configured as curved surface, the angle of the two tangent plane is γ, can be vertically arranged or be obliquely installed for the downside of expanding blowing area, rear spiral case 42b or its tangent plane with housing simultaneously.As shown in figure 11, the downside of rear spiral case 42b or its tangent plane and housing is φ.Usually, when unit design air-out region is in the same area with return air region, φ is acute angle, and when unit return air region and air-supply region are in zones of different, φ is obtuse angle.Preferably span is 30～170 °.With above-mentioned testing machine, when hoisting height 2.5 meters, the most high-grade air quantity be 634 cubic metres per hour, adjust angle φ, obtain the experimental result as shown in following table five.
Can draw from the experimental result of following table five, when angle φ is too small, there is backflow phenomenon, affect heat pump performance.And when φ is too small or during transition, when i.e. going up φ ＜ 30 ° or φ ＞ 170 ° in table, makes minimum air-supply height raise, and the height on the perigee distance ground that i.e. wind energy enough reaches constantly increases, and affects airflow effects.With minimum air-supply height less than 0.2mm as index, angle φ is most preferably in the range of 50 ° to 150 °.
Table five: the air-supply situation under different φ angles
As shown in figure 11, rear spiral case 42b is from the separation that the closest approach of tubular wine wheel 41 is air intake and air-out, when φ mono-timing, angle ω that rear spiral case 42b becomes with horizontal line from the line of tubular wine wheel 41 closest approach with tubular wine wheel 41 center of circle controls the ratio in air intake region and air-out region, when ω is bigger than normal, air intake district is less than normal, unit air quantity is little, and air-out is unstable, when ω is less than normal, air-out region is too small causes unit air quantity little, and the span of general ω is 40 °～120 °
Air-conditioner using a specified refrigerating capacity as 3.5kw is as testing machine, its fan blade diameter 108mm, 24 ° of tubular wine wheels of diffusion portion angle 41 and front spiral case gap delta 1=6mm, tubular wine wheel 41 and rear spiral case gap delta 2=5mm, use two-fold heat exchanger, it is 6 diameter 5mm heat exchange U pipes and 10 diameter 5mm heat exchange U pipes respectively, use different ω angles, when air-conditioner operates in the most high-grade, the test data of air quantity are such as shown in following table six (angular unit degree, air quantity cubic unit rice is per hour):
Table six: the experimental data of the air quantity under different ω angles
| ω | The most high-grade air quantity of unit |
| 40 | 546 |
| 60 | 582 |
| 80 | 628 |
| 100 | 623 |
| 120 | 575 |
Can draw from the data of upper table six, when ω from 40 ° constantly increase to 120 ° during, unit the most high-grade air quantity first increases and then decreases, when ω is 60 °～100 °, air quantity obtains the relatively figure of merit.
As shown in figure 11, tubular wine wheel 41 center of circle directly control the diffusion length of unit to distance L of the bottom of air outlet 12, when diffusion length too in short-term, stable air-out can not be formed, and air-out volume is low, and be easily accessible the stall zone of tubular wine wheel 41, when diffusion length is oversize, the diffusion pressure loss is excessive, and unit air quantity is low, and the span of general L is: 60mm≤L≤180mm.
Air-conditioner using a specified refrigerating capacity as 3.5kw is as testing machine, select fan blade diameter 98mm, diffusion portion angle 24 °, flow inlet angle α=184 °, give vent to anger angle beta=176 °, tubular wine wheel 41 and front spiral case gap delta 1=6mm, tubular wine wheel 41 and rear spiral case gap delta 2=5mm, use two-fold heat exchanger, wind is not 6 diameter 5mm heat exchange U pipes and 10 diameter 5mm heat exchange U pipes, uses different L, when air-conditioner operates in the most high-grade, the test data of air quantity are such as shown in following table seven (long measure is millimeter, and air quantity cubic unit rice is per hour):
Table seven: the experimental data of the air quantity under different L
| L | Air quantity | Remarks |
| 60 | 410 | Air-out volume is unstable |
| 98 | 594 | |
| 120 | 617 | |
| 140 | 573 | |
| 180 | 445 |
Can draw from the data of upper table seven, when L is during 60mm constantly increases to 180mm, unit the most high-grade air quantity first increases and then decreases, and when L is too small, the problem that air-out volume is unstable can be caused.Considering, when the L scope at 98mm～140mm, air quantity obtains the relatively figure of merit.
Preferably, as shown in figure 12, the return air inlet 11 of air pipe indoor machine includes the rear return air inlet 11a being arranged on housing 10 trailing flank and the upper return air inlet 11b of the upper side being arranged on housing 10；Air pipe indoor machine also includes the return air cover plate 13 arranged on the housing 10, and return air cover plate 13 has and covers return air inlet 11b and make air pipe indoor machine from the primary importance of rear return air inlet 11a return air；Make air pipe indoor machine from the second position of upper return air inlet 11b return air with covering rear return air inlet 11a；And open the 3rd position making air pipe indoor machine from upper return air inlet 11b and rear return air inlet 11a return air simultaneously.By the setting of return air cover plate 13, thus realize multiple return air form.Cover rear return air inlet 11a and to cover the return air cover plate of return air inlet 11b can be two independent parts, from improve part versatility and cost-effective from the point of view of, rear return air inlet 11a will be covered and to cover the return air deck design of upper return air inlet 11b be a general part, i.e. return air cover plate 13 both can cover rear return air inlet 11a, it is also possible to covers return air inlet 11b.
Preferably, as shown in Figure 6, between heat exchanger 20 and blower fan 40, it is provided with electric heater unit 50, when heat exchanger 20 can not meet heating needs, electric heater unit 50 can be started and make up the under powered problem of heat exchanger 20.
As can be seen from the above description, the above embodiments of the present invention achieve following technique effect:
Air pipe indoor machine according to the present invention, air outlet is arranged on the downside of housing, and the diffusion portion of blower fan is arranged directly down, so that air pipe indoor machine air-out directly down, efficiently solve common air pipe indoor machine to need that airduct is installed and just can make the downward problem of air-out direction, and improve air-out efficiency and the comfortableness heated.
The foregoing is only the preferred embodiments of the present invention, be not limited to the present invention, for a person skilled in the art, the present invention can have various modifications and variations.All within the spirit and principles in the present invention, any modification, equivalent substitution and improvement etc. made, should be included within the scope of the present invention.
Claims (23)
1. an air pipe indoor machine, including housing (10), described housing (10) is internal is fixedly installed heat exchanger (20), the side of described heat exchanger (20) is provided with blower fan (40), return air inlet (11) and the air outlet (12) laying respectively at described heat exchanger (20) both sides it is provided with on described housing (10), it is characterized in that, described air outlet (12) is arranged on the downside of described housing (10)；
Described return air inlet (11) includes the rear return air inlet (11a) being arranged on described housing (10) trailing flank and is arranged on the upper return air inlet (11b) of upper side of described housing (10)；
Described air pipe indoor machine also includes the return air cover plate (13) being arranged on described housing (10), and described return air cover plate (13) has and covers described upper return air inlet (11b) and make described air pipe indoor machine from the primary importance of described rear return air inlet (11a) return air；Make described air pipe indoor machine from the second position of described upper return air inlet (11b) return air with covering described rear return air inlet (11a)；And open and make described air pipe indoor machine from described upper return air inlet (11b) and the 3rd position of described rear return air inlet (11a) return air simultaneously；
Described blower fan (40) is cross flow fan, and the flow inlet angle of described cross flow fan is α, wherein, and 120 °≤α≤250 °；The efflux angles of described cross flow fan is β, wherein, and 110 °≤β≤240 °, and alpha+beta≤360 °.
Air pipe indoor machine the most according to claim 1, it is characterised in that
Described heat exchanger (20) is arranged on the inlet side of described blower fan (40), and the diffusion portion (43) of described blower fan (40) is down-set.
Air pipe indoor machine the most according to claim 2, it is characterised in that
The tubular wine wheel (41) and spiral case (42) arranged including cooperating, described spiral case (42) is equipped with at described housing (10) internal；
Described spiral case (42) includes the front spiral case (42a) forming side, described diffusion portion (43) first and the rear spiral case (42b) forming side, described diffusion portion (43) second.
Air pipe indoor machine the most according to claim 3, it is characterised in that
Angle between described front spiral case (42a) and described rear spiral case (42b) opens to air side, forms the diffusion angle γ of described diffusion portion (43), wherein, 10 °≤γ≤40 °.
Air pipe indoor machine the most according to claim 4, it is characterised in that 18 °≤γ≤28 °.
Air pipe indoor machine the most according to claim 3, it is characterised in that
Before the Edge Distance of described tubular wine wheel (41), the minimum clearance of spiral case (42a) is δ 1, wherein 3mm≤δ 1≤13mm；
After the Edge Distance of described tubular wine wheel (41), the minimum clearance of spiral case (42b) is δ 2, wherein 3mm≤δ 2≤15mm.
Air pipe indoor machine the most according to claim 6, it is characterised in that
5mm≤δ1≤8mm；
4mm≤δ2≤9mm。
Air pipe indoor machine the most according to claim 1, it is characterised in that
160°≤α≤190°；
170°≤β≤200°。
Air pipe indoor machine the most according to claim 3, it is characterised in that
The lower section of described heat exchanger (20) is provided with drip tray (30), is provided with thermal insulating filler (60) between described drip tray (30) and described housing (10)；
Thermal insulating filler (60) it is provided with between described spiral case (42) and described housing (10).
Air pipe indoor machine the most according to any one of claim 1 to 3, it is characterised in that described heat exchanger (20) is single folding heat exchanger.
11. air pipe indoor machine according to any one of claim 1 to 3, it is characterised in that
Described heat exchanger (20) is two folding heat exchangers, and described two folding heat exchangers include interconnective first heat exchanging part and the second heat exchanging part, has angle theta 1, wherein, 20 °≤θ 1≤150 ° between described first heat exchanging part and described second heat exchanging part.
12. air pipe indoor machine according to claim 11, it is characterised in that 35 °≤θ 1≤100 °.
13. air pipe indoor machine according to claim 11, it is characterised in that described two folding heat exchanger one bending formings, or by two separate exchangers spicing forming types.
14. air pipe indoor machine according to any one of claim 1 to 3, it is characterised in that described heat exchanger (20) is the many foldings heat exchanger more than two foldings.
15. air pipe indoor machine according to claim 14, it is characterised in that described many folding heat exchanger one bending formings, or by multiple separate exchangers spicing forming types.
16. air pipe indoor machine according to claim 14, it is characterised in that between two discharging the retained water of the arbitrary neighborhood of described many folding heat exchangers, there is angle theta 2, wherein, 0 °≤θ 2≤180 °.
17. according to the air pipe indoor machine described in Claims 2 or 3, it is characterised in that in included angle between outer contour and the downside of described housing of described diffusion portion (43), wherein, 30 °≤φ≤170 °.
18. air pipe indoor machine according to claim 17, it is characterised in that 50 °≤φ≤150 °.
19. air pipe indoor machine according to claim 3, it is characterized in that, the described rear spiral case (42b) line from the center of circle of closest approach and the described tubular wine wheel (41) of described tubular wine wheel (41) is ω with horizontal angle, wherein, 40 °≤ω≤120 °.
20. air pipe indoor machine according to claim 19, it is characterised in that 60 °≤ω≤100 °.
21. air pipe indoor machine according to claim 3, it is characterised in that
The center of circle of described tubular wine wheel (41) is L to described air outlet (12) the vertically distance on the downside of described housing (10), wherein, and 60mm≤L≤180mm.
22. air pipe indoor machine according to claim 21, it is characterised in that 98mm≤L≤140mm.
23. air pipe indoor machine according to any one of claim 1 to 3, it is characterised in that be provided with electric heater unit (50) between described heat exchanger (20) and described blower fan (40).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210194813.XA CN103486661B (en) | 2012-06-13 | 2012-06-13 | Air pipe indoor unit |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210194813.XA CN103486661B (en) | 2012-06-13 | 2012-06-13 | Air pipe indoor unit |
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| Publication Number | Publication Date |
|---|---|
| CN103486661A CN103486661A (en) | 2014-01-01 |
| CN103486661B true CN103486661B (en) | 2016-08-03 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201210194813.XA Active CN103486661B (en) | 2012-06-13 | 2012-06-13 | Air pipe indoor unit |
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Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105180287B (en) * | 2015-10-12 | 2018-09-07 | 珠海格力电器股份有限公司 | Through-flow air duct type air conditioning unit and air supply method |
| CN106287982B (en) * | 2016-09-19 | 2018-09-07 | 珠海格力电器股份有限公司 | Bottom shell structure of indoor unit, indoor unit and method for improving noise of indoor unit |
| CN107655074A (en) * | 2017-09-27 | 2018-02-02 | 珠海格力电器股份有限公司 | Air conditioner |
| CN109353186A (en) * | 2018-11-27 | 2019-02-19 | 珠海格力电器股份有限公司 | Air conditioning system and vehicle with same |
| CN114396657B (en) * | 2022-01-10 | 2024-07-19 | 珠海格力节能环保制冷技术研究中心有限公司 | Distributed air supply device, refrigeration system and control method of refrigeration system |
| CN114370667A (en) * | 2022-01-10 | 2022-04-19 | 珠海格力电器股份有限公司 | Air duct machine and distributed air supply device |
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| CN101031753A (en) * | 2004-09-30 | 2007-09-05 | 东芝开利株式会社 | Air conditioner |
| EP1243864B1 (en) * | 2001-03-23 | 2007-10-10 | Mitsubishi Heavy Industries, Ltd. | Indoor unit and air-conditioner |
| CN101182941A (en) * | 2006-11-15 | 2008-05-21 | 三星电子株式会社 | 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 |
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| EP1243864B1 (en) * | 2001-03-23 | 2007-10-10 | Mitsubishi Heavy Industries, Ltd. | Indoor unit and air-conditioner |
| CN101031753A (en) * | 2004-09-30 | 2007-09-05 | 东芝开利株式会社 | Air conditioner |
| CN101182941A (en) * | 2006-11-15 | 2008-05-21 | 三星电子株式会社 | 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 |
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| CN103486661A (en) | 2014-01-01 |
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