CN105953306A - Indoor Unit of Air Conditioner and Air Conditioner Including the Same - Google Patents
Indoor Unit of Air Conditioner and Air Conditioner Including the Same Download PDFInfo
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- CN105953306A CN105953306A CN201510955742.4A CN201510955742A CN105953306A CN 105953306 A CN105953306 A CN 105953306A CN 201510955742 A CN201510955742 A CN 201510955742A CN 105953306 A CN105953306 A CN 105953306A
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- China
- Prior art keywords
- air
- mentioned
- centrifugal fan
- heat exchanger
- indoor set
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
- F24F1/0022—Centrifugal or radial fans
-
- 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
- F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
- F24F1/0047—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in the ceiling or at the ceiling
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
- F24F1/032—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by heat exchangers
- F24F1/0325—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
-
- 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
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/26—Refrigerant piping
- F24F1/32—Refrigerant piping for connecting the separate outdoor units to indoor units
-
- 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
- F24F13/08—Air-flow control members, e.g. louvres, grilles, flaps or guide plates
-
- 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
- F24F13/02—Ducting arrangements
- F24F13/06—Outlets for directing or distributing air into rooms or spaces, e.g. ceiling air diffuser
- F24F2013/0616—Outlets that have intake openings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
- Devices For Blowing Cold Air, Devices For Blowing Warm Air, And Means For Preventing Water Condensation In Air Conditioning Units (AREA)
- Air-Flow Control Members (AREA)
Abstract
An indoor unit of an air conditioner of the present invention includes a cabinet; an air inlet through which air is sucked into the cabinet; a centrifugal fan which blows the air sucked in to the surrounding portions; and an a heat exchanger which is provided in the direction of air supply of the centrifugal fan and allows heat exchange between the air and a refrigerant flowing thereinside, in which the following equation is satisfied: 0.16<=L/D<=0.19, where D is an outer diameter of the centrifugal fan and L is a distance between the centrifugal fan and the heat exchanger in their closest positions. Thus, a variation in a velocity distribution created in the heat exchanger can be suppressed, and the indoor unit of the air conditioner which achieves an improved energy saving property due to a reduced pressure loss and an improved heat exchange efficiency of the heat exchanger can be provided.
Description
Technical field
The indoor set that the present invention relates to air-conditioning device and the air-conditioning device including this indoor set.
Background technology
Japanese Unexamined Patent Application Publication No. 2011-12937 (patent documentation 1) discloses sky
The indoor set adjusting device is including to send here from the fan of heat exchanger with fan side in opposite directions
Air is towards the guiding parts of heat exchanger lower guide.
The heat exchanger that indoor set is carried is for improving heat exchanger effectiveness and reducing the pressure loss
And maximize.The outlet height of the aspect ratio centrifugal fan of heat exchanger is bigger.If additionally,
Carry centrifugal fan in the confined space of indoor set, then centrifugal fan will necessarily be equipped on heat friendship
Parallel operation top.In view of this situation, the velocity flow profile of internal heat exchanger can produce variation.
Therefore, as the composition of patent documentation 1, by arranging with fan side in opposite directions
By the air sent from fan towards the guiding parts of heat exchanger lower guide, it is possible to suppression exists
The velocity flow profile variation that internal heat exchanger produces.
Although installing the such means of guiding parts around centrifugal fan can suppress in heat exchange
The velocity flow profile variation produced in device, but be not suppression variation generation itself, it is impossible to fully
Realize the further raising of efficiency and energy-conservation aspect.
Then, the velocity flow profile that it is an object of the invention to suppress to produce at internal heat exchanger becomes
Move and a kind of indoor set realizing the air-conditioning device that energy saving improves is provided.
Summary of the invention
In order to solve above-mentioned problem, the indoor set of the air-conditioning device of the present invention, it is characterised in that
Including: framework；The air entry of air is sucked in above-mentioned framework；Blow to peripheral part and inhaled
The centrifugal fan of the air entered；And be located at the air supply direction of above-mentioned centrifugal fan and make above-mentioned sky
Gas and the heat exchanger carrying out heat exchange at the cold-producing medium of internal flow, meet relationship below:
0.16≤L/D≤0.19,
Wherein D is the external diameter of above-mentioned centrifugal fan, and L is above-mentioned centrifugal fan and above-mentioned heat exchange
Immediate distance between device.
According to the present invention, the velocity flow profile variation produced at internal heat exchanger can be suppressed, it is possible to
The pressure loss because reducing heat exchanger and raising heat exchanger effectiveness is provided to realize energy saving and carry
The indoor set of high air-conditioning device.
Other problems of the present invention, constitute, act on, effect will be the most detailed
Describe in detail bright.
Accompanying drawing explanation
Fig. 1 is the axonometric chart of the indoor set of the air-conditioning device involved by embodiments of the present invention；
Fig. 2 be the indoor set of the air-conditioning device involved by embodiments of the present invention relative to from
The sectional view that heart fan rotation axis is vertical；
Fig. 3 is the A-A section of the indoor set of the air-conditioning device shown in Fig. 2；
Fig. 4 be transverse axis be L/D, the longitudinal axis be the mark of velocity flow profile produced at internal heat exchanger
The curve chart of quasi-difference；
Fig. 5 be transverse axis be b2/H, the longitudinal axis be the mark of velocity flow profile produced at internal heat exchanger
The curve chart of quasi-difference；
Fig. 6 is the view representing the region between centrifugal fan and heat exchanger；
Fig. 7 be exaggerated in Fig. 3 filter, horn mouth, the sectional view of centrifugal fan；
Fig. 8 is conventional filter, horn mouth, the sectional view of centrifugal fan.
Detailed description of the invention
Following with accompanying drawing, embodiments of the present invention are illustrated.
[the 1st embodiment]
Fig. 1 represents the solid of the indoor set of the air-conditioning device involved by embodiments of the present invention
Figure.The indoor set of Fig. 1 is connected with off-premises station (not shown) via refrigerant piping, constitutes sky
Adjust device.It is equipped with compressor at off-premises station.By this compressor compresses cold-producing medium, by
Circulate in refrigerant piping and form kind of refrigeration cycle.Indoor set includes the framework being arranged in ceiling
1 and be arranged on the panel 2 of indoor of framework 1.Panel 2 is provided with and is taken into room air
Grid 3 and four for the air that will suck from grid 3 towards the gas outlet 5 of indoor blowout.?
Respectively can pacify in the way of being driven rotation by used in blinds motor (not shown) on gas outlet 5
Equipped with shutter 4, with this, blow-off direction of air is adjusted.In other words, panel 2 has
There is the air inlet drawn air in framework 1.
Fig. 2 is to represent the indoor that Fig. 1 is watched in the direction of rotary shaft Z (Fig. 3) towards fan
The view of the sectional view of machine.As shown in Figure 2, the indoor set of present embodiment has: tool
Have and be arranged in indoor set central part and towards leaf after away from the direction air-out of rotary shaft Z
The centrifugal fan 10 of sheet；It is configured to the air supply direction at centrifugal fan 10 and surrounds centrifugal fan 10
And carry out from the air of centrifugal fan 10 and the heat exchange between the cold-producing medium of internal flow
Heat exchanger 11.
The shape of heat exchanger 11 is to cut open with vertical relative to rotary shaft Z of centrifugal fan 10
There are during view viewing the polygon of curvature, substantially four opened in a part of corner in corner
Limit shape.In fig. 2, heat exchanger 11 presents and surrounds centrifugal with corner at three and four line parts
The shape of fan 10.One of them corner has the rectilinear form more shorter than other line parts, becomes
For the shape that distance between self and the peripheral part of centrifugal fan 10 compared with other corners is shorter
Shape.Although not shown, but in the space being located between this corner and framework 1, it is arranged in refrigeration
Drainage pump during operating, the dew (drain water) produced at heat exchanger 11 discharged.
Fig. 3 is the view representing the A-A section in Fig. 2.By being connected with centrifugal fan 10
Motor 20 make centrifugal fan 10 rotate centered by rotary shaft Z, thus through being installed on lattice
The filter 6 of grid 3 sucks air.The air sucked is through the opening towards centrifugal fan 10
The diminishing horn mouth in portion 12, by centrifugal fan 10 to the radial direction (week of centrifugal fan 10
To) blowout.The air being blown is through over-heat-exchanger 11, after heat exchanger 11 flows out,
It is discharged to indoor from gas outlet 5, thus forms the air-flow 50 shown in Fig. 3.When air-flow 50
Shown air from gas outlet 5 to indoor blowout time, right by the shutter 4 being installed on panel 2
Wind direction is adjusted.
When heating operating or during cooling operation, make in a heat exchanger 11 air with in heat exchange
The cold-producing medium of the internal flow of device 11 carries out heat exchange, thus carry out the air of indoor heat or
Refrigeration.It is accommodated with the electric box 7 of the control substrate (not shown) of motor-driven work in control room
It is installed in the bottom of the horn mouth 12 as the space between filter 6 and horn mouth 12.
Then, to the centrifugal fan 10 in present embodiment and the size relationship of heat exchanger 11
Illustrate.
If the external diameter of centrifugal fan 10 is set to D, hang down in rotary shaft Z with centrifugal fan 10
In straight section, it is L (ginseng by centrifugal fan 10 and the immediate distance definition of heat exchanger 11
According to Fig. 2).When centrifugal fan 10 and the immediate distance of heat exchanger 11 are L, L/D is
Little.Heat exchanger 11 has four line parts, but between each line part and centrifugal fan 10
Distance L is roughly the same.
In the past, centrifugal fan was designed by and made the biggest footpath of centrifugal fan 10, thus dropped
Axle power under low same traffic.And in the present invention, be not only to realize big footpath, and
It is in order at and realizes heat by reduction through the variation of the flow velocity of the air within over-heat-exchanger 11
The pressure loss of exchanger 11 reduces and the performance of heat exchange circulation improves such purpose,
Eye distance L between the outer diameter D and centrifugal fan 10 and heat exchanger 11 of centrifugal fan 10
Relation L/D.
Fig. 4 be transverse axis be L/D, the longitudinal axis be to represent the air of inside through over-heat-exchanger 11
The curve chart of the variation of velocity flow profile.Make the outlet height of centrifugal fan 10 illustrated in Fig. 3
B2 converts, and is represented by solid and broken lines the change of the different b2 standard deviation relative to L/D.If mark
Quasi-difference diminishes, then the variation of flow velocity through the air of the inside of over-heat-exchanger 11 diminishes, flow velocity
Distribution is close to uniformly.If velocity flow profile is close to uniformly, then the pressure loss of heat exchanger 11 reduces,
The effect that heat exchanger effectiveness improves can be obtained.In conventional device, such as L=54mm, D
=490mm, L/D=0.11, but the district of the L/D that standard deviation diminishes is understood according to this curve chart
The when that territory being 0.16≤L/D≤0.19.
Specifically, (L/D is little) is got too close at centrifugal fan 10 and heat exchanger 11
In the case of, centrifugal fan 10 uprises with the wind speed local of the proximity part of heat exchanger 11,
Velocity flow profile produces variation.On the other hand, excessively divide with heat exchanger 11 at centrifugal fan 10
In the case of (L/D is big), the outer diameter D of centrifugal fan 10 becomes relative to heat exchanger 11
Obtain the least, thus in order to carry identical air quantity in heat exchanger 11, need increase to be centrifuged wind
The rotating speed of fan 10.Along with the increase of rotating speed, circumferential speed increases, thus, from centrifugal wind
Fan 10 wind direction relative to the inflow face of heat exchanger 11 close to parallel, to velocity flow profile
Have a negative impact.Consider this point, based on Fig. 4, in the present embodiment, to become
The mode of 0.16≤L/D≤0.19 constitutes centrifugal fan 10 and heat exchanger 11.Further preferably
Be 0.17≤L/D≤0.18.Thereby, it is possible to greatly improve velocity flow profile, heat exchange can be improved
Efficiency.
It addition, in order to make L/D change (such as increasing L/D), there are following means: reduce
The external diameter of centrifugal fan 10；And expansion heat exchanger 11.Feelings at expansion heat exchanger 11
Under condition, the gas outlet 5 between framework 1 and heat exchanger 11 narrows, and the pressure loss increases, and send
Wind efficiency reduces.Concurrently there are in order to maintain the aperture area of gas outlet 5 and with heat exchange
The expansion of device 11 also makes the means that framework 1 maximizes.It is preferred, however, that the setting of indoor set
Space (especially ceiling embedded type) does not has the change in construction, does not change conventional framework chi
Very little the most substantially 840mm.Therefore, in addition to meeting the regulation of 0.16≤L/D≤0.19, also may be used
It is designed to meet 830mm≤W≤850mm with external dimensions W by framework 1.It addition, be
Bringing impact to the size of heat exchanger 11 and gas outlet 5, the outer diameter D of fan is excellent
Elect 440mm≤D≤470mm as.
[the 2nd embodiment]
Fig. 3 represents the outlet height b2 and the height H of heat exchanger 11 of centrifugal fan 10
Definition.Now, if by the height of the outlet height b2 of centrifugal fan 10 Yu heat exchanger 11
The ratio of degree H is set as b2/H, by b2/H is set to appropriate value, and can be by application above-mentioned the
1 embodiment improves the efficiency of centrifugal fan 10 further.
First, it is set to constant, to make centrifugal fan 10 row to by the height H of heat exchanger 11
The situation of outlet height b2 change illustrates.
If reducing the outlet height b2 of centrifugal fan 10, reduce b2/H, then by centrifugal fan
The flow path width that the hub face 101 of 10 and ground plane 102 are constituted reduces, and centrifugal fan 10 is internal
Friction loss increase, the efficiency of centrifugal fan 10 reduces.
On the other hand, if increasing the outlet height b2 of centrifugal fan 10, increase b2/H, then
The flow path width being made up of hub face 101 and ground plane 102 increases, and friction loss reduces.Centrifugal
Fan 10 has the feature that and sucks air from the lower section of Fig. 3 in rotary shaft Z-direction, presses
Take a picture and the vertical angle of rotary shaft Z or close angle are blown.To this end, it is excellent
Choosing is that the air making centrifugal fan 10 be sucked flows along ground plane 102.But, if by
The flow path width that hub face 101 and ground plane 102 are constituted increases, then centrifugal fan 10 is sucked
Air can depart from from ground plane 102, causes the efficiency of centrifugal fan 10 to reduce.
Then, to the outlet height b2 of centrifugal fan 10 is set as constant, make heat exchanger
The situation of the height H change of 11 illustrates.If reducing the height H of heat exchanger 11, increase
Big b2/H, then the heat transfer area of heat exchanger 11 reduces, and causes the reduction of heat exchanger effectiveness.
On the other hand, if increasing the height H of heat exchanger 11, b2/H, then heat exchange are reduced
The heat transfer area of device 11 increases, and heat exchanger effectiveness improves, but due to the height of heat exchanger 11
H is excessive, so the air-supply from centrifugal fan 10 becomes uneven.Its result, through overheated
Produce variation in the velocity flow profile of the air of the inside of exchanger 11, cause heat exchanger effectiveness to drop
Low.
Fig. 5 be transverse axis be b2/H, the longitudinal axis be represent through the air within over-heat-exchanger 11
The curve chart of the standard deviation of flow velocity variation.As Fig. 4, if standard deviation diminishes, then through overheated
The variation of the flow velocity of the air of the inside of exchanger 11 diminishes, and velocity flow profile is close to uniformly.According to
The when that the region of the b2/H that standard deviation knowable to this curve chart diminishes being 0.3≤b2/H≤0.5.
So, b2/H is excessive or too small all can cause the efficiency of centrifugal fan 10, heat exchanger
The heat exchanger effectiveness of 11 reduces.It is therefore preferable that 0.3≤b2/H≤0.5.It addition, more preferably
Be 0.35≤b2/H≤0.45.
[the 3rd embodiment]
Fig. 6 is the view representing the region between centrifugal fan and heat exchanger.Relative to from
In the vertical section of rotary shaft Z of heart-wind syndrome fan 10, will be handed over by the periphery of centrifugal fan 10, heat
The face that flows into of parallel operation 11, the circumferential end of connection heat exchanger 11 and the rotation of centrifugal fan 10
The straight line area encompassed at center, is set in Fig. 6 the region X represented with Lycoperdon polymorphum Vitt.
In the case of the outer diameter D of centrifugal fan 10 and the height H of heat exchanger 11 are identical,
Radial distance between centrifugal fan 10 and heat exchanger 11 is elongated, say, that in region
In the case of the area A of X expands, the inflow enlarged areas of heat exchanger 11.Owing to flowing into
The expansion of area, the heat transfer area of heat exchanger 11 expands, thus heat exchanger effectiveness is improved.
It addition, the pressure loss of heat exchanger 11 has become according to the flow velocity of the air internal through it
Change.To this end, by the expansion flowing into area, through air flat of the inside of over-heat-exchanger 11
All flow velocitys reduce, thus the pressure loss of heat exchanger 11 reduces, and the axle of centrifugal fan 10 moves
Power reduces.
According to above-mentioned 1st embodiment, by being set as 0.16≤L/D≤0.19, it is possible to reduce and pass through
The variation of the velocity flow profile of the air within heat exchanger 11.It is therefore desirable to heat exchanger 11
The raising of heat exchanger effectiveness and the reduction of the pressure loss.And then, if the face of enlarged area X
Long-pending A, namely expands area that external dimensions W according to framework 1 calculates with region X's
The ratio i.e. A/W of area A2, then can expect to improve heat exchanger effectiveness further and reduce pressure to damage
Lose.
But, if being set as 0.16≤L/D≤0.19, increase A/W2, then heat exchanger 11 can gradually
Expand towards outside.In this case, it is impossible to guarantee fully gas outlet 5 aperture area and
The width of gas outlet stream 8, causes their pressure loss to increase, causes and cannot play regulation
The Main Function of room air such air-conditioning device.For this reason, it is preferred that
0.21≤A/W2≤0.27。
[the 4th embodiment]
The 4th embodiment being obtained more effect by above-mentioned 1st embodiment of application is entered
Row explanation.
According to above-mentioned 1st embodiment, by being set as 0.16≤L/D≤0.19, it is possible to reduce and pass through
The variation of the velocity flow profile of the air within heat exchanger 11.But, at centrifugal fan 10
In the case of outer diameter D changes and makes L/D identical, need to make the change in size of heat exchanger 11.
When the ratio of the outer diameter D of centrifugal fan 10 with external dimensions W of framework 1 is set to D/W
Time, if reducing D/W, then diminish with the size of the heat exchanger 11 of D+2L definition.Meanwhile,
The girth of heat exchanger 11 shortens.Then, heat transfer area reduces, and heat exchanger effectiveness is deteriorated.
On the other hand, if increasing D/W, becoming large-sized of heat exchanger 11 the most defined above,
Heat transfer area increases.Although this makes heat exchanger effectiveness improve, but the stream width of gas outlet stream 8
Degree reduces.The area of gas outlet 5 cannot be substantially ensured that, thus the pressure loss of gas outlet 5 increases
Greatly.
To this end, in order to by applying above-mentioned 1st embodiment to obtain effect further and preferred
Be 0.52≤D/W≤0.56.
[the 5th embodiment]
Fig. 8 be do not apply filter 6 in the case of embodiment of the present invention, horn mouth 12a,
The sectional view of centrifugal fan 10.Horn mouth 12a is in order to import air, shape to centrifugal fan 10
Become from inlet diameter Db1Towards going out bore Db2Make the structure that aperture area tapers into.As
As shown in Figure 8, face 13 and the horn mouth 12a of filter 6 it is parallel at horn mouth 12a
The connection of peristome constituted with a circular arc in the case of, set high horn mouth 12a if insufficient
Height Hb, then the inlet diameter D of horn mouth 12ab1Diminish, the enlarged areas in face 13.
Filter 6 is less than other parts with the distance in face 13, through the filter 6 overlapping with face 13
The flow-rate ratio of air in region few through the flow of the air of filter 6 central authorities.To this end, face
The area of 13 is more for expanding, and flow field 51 the most as shown in Figure 8 is such, through filter 6
The flow of air exists for the tendency the most in filter 6 center.
Fig. 7 be apply filter 6 in the case of embodiment of the present invention, horn mouth 12,
The sectional view of centrifugal fan 10.Horn mouth 12 includes inclined plane 12b with constant inclination angle
Dough-making powder 13.Face 13 is parallel to filter 6.It is to say, the peristome of horn mouth 12b is set
Tapered (being set as butt conical hollow).Even without the height H fully obtaining horn mouth 12b,
It also is able to the inlet diameter of horn mouth 12b from Db1Expand D tob1’.Meanwhile, it is capable to reduce
The area in face 13.Its result, flow field 52 as shown in Figure 7 is such, by increasing capacitance it is possible to increase passed through
The flow of the air of the end of filter 6, through the flow of air of filter 6 at filter 6
On the whole close to uniformly, so the pressure loss of filter 6 can be reduced.
Claims (9)
1. the indoor set of an air-conditioning device, it is characterised in that including:
Framework；
The air entry of air is sucked in above-mentioned framework；
The centrifugal fan of sucked air is blowed to peripheral part；And
It is located at the air supply direction of above-mentioned centrifugal fan and makes above-mentioned air and the refrigeration in internal flow
Agent carries out the heat exchanger of heat exchange,
Meet relationship below:
0.16≤L/D≤0.19,
Wherein D is the external diameter of above-mentioned centrifugal fan, and L is above-mentioned centrifugal fan and above-mentioned heat exchange
Immediate distance between device.
The indoor set of air-conditioning device the most according to claim 1, it is characterised in that
Meet relationship below:
835mm≤W≤845mm,
Wherein W is the external dimensions of above-mentioned framework.
The indoor set of air-conditioning device the most according to claim 1, it is characterised in that
The outer diameter D of above-mentioned centrifugal fan meets relationship below:
440mm≤D≤470mm。
The indoor set of air-conditioning device the most according to claim 2, it is characterised in that
The outer diameter D of above-mentioned centrifugal fan meets relationship below:
440mm≤D≤470mm。
The indoor set of air-conditioning device the most according to claim 1, it is characterised in that
Meet relationship below:
0.3≤b2/H≤0.5,
Wherein b2 is the outlet height of above-mentioned centrifugal fan, and H is the height of above-mentioned heat exchanger
Degree.
The indoor set of air-conditioning device the most according to claim 1, it is characterised in that
Meet relationship below:
A/W20.21,
Wherein W is the external dimensions of above-mentioned framework, and A is in the rotation relative to above-mentioned centrifugal fan
The section that rotating shaft is vertical is flowed into above-mentioned heat exchanger by the outer peripheral lines of above-mentioned centrifugal fan, air
Face interior contour and by the rotation of the circumferential end of above-mentioned heat exchanger Yu above-mentioned centrifugal fan
The area of the straight line area defined that center connects.
The indoor set of air-conditioning device the most according to claim 1, it is characterised in that
Meet relationship below:
0.52≤D/W≤0.56,
Wherein W is the external dimensions of above-mentioned framework.
The indoor set of air-conditioning device the most according to claim 1, it is characterised in that
It is also equipped with the loudspeaker that will guide towards above-mentioned centrifugal fan from above-mentioned air entry leaked-in air
Mouthful,
Above-mentioned horn mouth has curved face part and inclined plane, and above-mentioned curved face part is at bell-mouthed opening surface
Amassing and be bent upwards towards the side that above-mentioned air entry expands, above-mentioned inclined plane has to be opened bell-mouthed
Open area is from the acclivitous shape in the side that above-mentioned curved face part expands further.
9. an air-conditioning device, it is characterised in that including:
According to the indoor set any one of claim 1 to 7；
Off-premises station；And
Connect the pipe arrangement of indoor set and off-premises station.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015037610A JP6363033B2 (en) | 2015-02-27 | 2015-02-27 | Air conditioner indoor unit and air conditioner equipped with the same |
| JP2015-037610 | 2015-02-27 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105953306A true CN105953306A (en) | 2016-09-21 |
Family
ID=56798211
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510955742.4A Pending CN105953306A (en) | 2015-02-27 | 2015-12-18 | Indoor Unit of Air Conditioner and Air Conditioner Including the Same |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US20160252259A1 (en) |
| JP (1) | JP6363033B2 (en) |
| CN (1) | CN105953306A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107036166A (en) * | 2017-04-18 | 2017-08-11 | 青岛海尔空调器有限总公司 | Indoor apparatus of air conditioner |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7329969B2 (en) * | 2019-06-06 | 2023-08-21 | シャープ株式会社 | air conditioner |
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| JP3724273B2 (en) * | 1999-09-20 | 2005-12-07 | 三菱電機株式会社 | Blower, blower system, blower method of blower system |
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- 2015-12-17 US US14/973,190 patent/US20160252259A1/en not_active Abandoned
- 2015-12-18 CN CN201510955742.4A patent/CN105953306A/en active Pending
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| CN86102055A (en) * | 1985-03-29 | 1986-12-03 | 三菱电机株式会社 | Air conditioner |
| JPH0539930A (en) * | 1991-08-02 | 1993-02-19 | Daikin Ind Ltd | Air conditioner |
| JPH10176861A (en) * | 1996-12-16 | 1998-06-30 | Mitsubishi Heavy Ind Ltd | Air-conditioner |
| CN1143989C (en) * | 1998-07-29 | 2004-03-31 | 株式会社日立制作所 | Indoor machine for built-in ceiling type |
| JP2000304347A (en) * | 1999-04-22 | 2000-11-02 | Mitsubishi Electric Corp | Heat exchanging unit |
| CN1282861A (en) * | 1999-07-28 | 2001-02-07 | 三星电子株式会社 | Bell type opening device of ceiling type air conditioner |
| JP2001248854A (en) * | 2000-03-08 | 2001-09-14 | Daikin Ind Ltd | Air conditioner |
| US20040244403A1 (en) * | 2003-06-03 | 2004-12-09 | Samsung Electronics Co., Ltd. | Turbofan and air conditioner having the turbofan |
| JP2005114321A (en) * | 2003-10-10 | 2005-04-28 | Sanyo Electric Co Ltd | Ceiling embedded type air conditioner |
| CN101802509A (en) * | 2007-10-25 | 2010-08-11 | 东芝开利株式会社 | Ceiling-embedded air conditioner |
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| JP2011252672A (en) * | 2010-06-03 | 2011-12-15 | Mitsubishi Electric Corp | Indoor unit of air conditioner |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107036166A (en) * | 2017-04-18 | 2017-08-11 | 青岛海尔空调器有限总公司 | Indoor apparatus of air conditioner |
| CN107036166B (en) * | 2017-04-18 | 2020-02-04 | 青岛海尔空调器有限总公司 | Indoor unit of air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| US20160252259A1 (en) | 2016-09-01 |
| JP6363033B2 (en) | 2018-07-25 |
| JP2016161152A (en) | 2016-09-05 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20180710 Address after: Tokyo, Japan, Japan Applicant after: Hitachi Johnson Controls Air Conditioning Co., Ltd. Address before: Hongkong, China Applicant before: Johnson Controls Hitachi air conditioning technology (Hongkong) Co., Ltd. |
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| TA01 | Transfer of patent application right | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20160921 |
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| RJ01 | Rejection of invention patent application after publication |