CN104422029A - Air conditioner indoor unit and air conditioner using the indoor unit - Google Patents
Air conditioner indoor unit and air conditioner using the indoor unit Download PDFInfo
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- CN104422029A CN104422029A CN201410389250.9A CN201410389250A CN104422029A CN 104422029 A CN104422029 A CN 104422029A CN 201410389250 A CN201410389250 A CN 201410389250A CN 104422029 A CN104422029 A CN 104422029A
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- 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
- F24F1/0025—Cross-flow or tangential fans
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- 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
- F24F13/10—Air-flow control members, e.g. louvres, grilles, flaps or guide plates movable, e.g. dampers
- F24F13/14—Air-flow control members, e.g. louvres, grilles, flaps or guide plates movable, e.g. dampers built up of tilting members, e.g. louvre
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/24—Means for preventing or suppressing noise
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/30—Arrangement or mounting of heat-exchangers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/24—Means for preventing or suppressing noise
- F24F2013/247—Active noise-suppression
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2221/00—Details or features not otherwise provided for
- F24F2221/22—Cleaning ducts or apparatus
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- 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)
Abstract
Angle-interval between same parts of adjacent blade pairs is determined by a specified mathematic form, which has the following the problems: frequency based on an average distance has the tendency of becoming a main guide, noise under specific frequency is high, and comfortability is not increased. The invention aims to provide an air conditioner indoor unit with a cross flow fan capable of reducing noise, comprising an indoor heat exchanger, and a cross flow fan arranged downstream the indoor heat exchanger and provided with a plurality of fan blades with waveform or serriform external diameters, wherein blade pitches of the fan blades and the cross flow fan increase and decrease roughly periodically.
Description
Technical field
The present invention relates to air regulator.
Background technology
In patent document 1, record the impeller after a kind of improvement of Horizontal-type fan, its adjacent blade is determined by the mathematical expression specified the angle intervals between upper same position.In the impeller of the Horizontal-type fan described in patent document 1, adjacent blade becomes the cycle of being expressed by trigonometric function to the angle intervals between upper same position, thus effectively can reduce the noise of blade velocity sound when not upsetting static balancing and dynamic equilibrium.
[patent document 1] Japanese Unexamined Patent Publication 6-294396 publication
But the impeller described in patent document 1 exists following problem: the frequency based on average headway exists into the tendency of taking as the leading factor, the noise under specific frequency increases, and comfortableness does not improve.
Summary of the invention
The object of the present invention is to provide a kind of indoor set possessing the air regulator of the axial-flow fan reducing noise.
The indoor set of air regulator of the present invention possesses: indoor heat converter; And axial-flow fan, the downstream of its heat exchanger disposed in the interior, has multiple fan blade that outer diameter shape is waveform or saw shape, wherein, and the position that fan blade increases and decreases with being configured in the blade pitgh approximate period property of axial-flow fan.
[invention effect]
According to the present invention, a kind of indoor set possessing the air regulator of the axial-flow fan reducing noise can be provided.
Accompanying drawing explanation
Fig. 1 is the loop structure figure of the air regulator of the first embodiment.
Fig. 2 is a main TV structure figure when part for the indoor set of the air regulator of the first embodiment being had an X-rayed.
Fig. 3 is the sectional structure chart of the indoor set of the air regulator of the first embodiment.
Fig. 4 is the stereogram of axial-flow fan one section of the indoor set of the air regulator of the first embodiment.
Fig. 5 represents the arrangement of the blade pitgh of the fan blade of the axial-flow fan of the indoor set of the air regulator of the first embodiment.
Fig. 6 represents the measurement result of the frequency of the indoor set of the air regulator of comparative example 1 and comparative example 2 and the relation of noise.
Fig. 7 represents the measurement result of the frequency of the indoor set of the air regulator of comparative example 1 and comparative example 3 and the relation of noise.
Fig. 8 represents the measurement result of the frequency of the indoor set of the air regulator of the first embodiment and comparative example 3 and the relation of noise.
Fig. 9 represents the Numerical results of the instantaneous value of the pressure distribution in the stabilizer of comparative example 3.
Figure 10 represents the Numerical results of the instantaneous value of the pressure distribution in the stabilizer of the first embodiment.
Figure 11 is the key diagram of the flowing close to the wind speed in fan blade during stabilizer that the first embodiment is described.
Figure 12 is the key diagram of the flowing close to the wind speed in fan blade during stabilizer that the second embodiment is described.
Figure 13 is the key diagram of the flowing close to the wind speed in fan blade during stabilizer that the 3rd embodiment is described.
[symbol description]
100 ... indoor set, 120 ... indoor heat converter, 122 ... preceding heat exchanger, 130 ... axial-flow fan, 131 ... procapsid, 201 ... stabilizer, 132 ... back casing, 202 ... rear guiding piece, 310 ... fan blade, 311 ... edge, 312 ... peak, 313 ... paddy.
Detailed description of the invention
Suitable to accompanying drawing, embodiments of the present invention are described in detail.It should be noted that, to part common in each figure mark same symbol, and the repetitive description thereof will be omitted.
(the first embodiment)
Fig. 1 is the loop structure figure of the air regulator of the first embodiment.When cooling operation, from compressor 1 spray high temperature and the cold-producing medium of high pressure flow into outdoor heat exchanger 3 via cross valve 2.Flow into cold-producing medium in outdoor heat exchanger 3 and carry out heat exchange with the air of the outdoor of being carried by outdoor blower fan 4, thus condensation and become liquid refrigerant.Liquid refrigerant, by expansion valve 5, becomes the two-phase system cryogen of low-temp low-pressure thus and flows into indoor heat converter 120.
Flow into the two-phase system cryogen of the low-temp low-pressure in indoor heat converter 120 and carry out heat exchange by the air of axial-flow fan (indoor blower fan) 130 indoor of carrying.Now, be transported to the two-phase refrigerant cools of air by the low-temp low-pressure flow in indoor heat converter 120 of the indoor of indoor heat converter 120, and from blow-off outlet to indoor ejection.Temperature from from blow-off outlet to the air of the air ratio suction inlet of indoor ejection is low, therefore, it is possible to reduce indoor temperature.Cold-producing medium carry out heat exchange in indoor heat converter 120 after turns back to compressor 1 again via cross valve 2.Compressor 1, outdoor heat converter 3, outdoor blower fan 4 and expansion valve 5 are configured at off-premises station, and indoor heat converter 120 and axial-flow fan 130 are configured at indoor set 100.
Fig. 2 is a main TV structure figure when part for the indoor set of the air regulator of the first embodiment being had an X-rayed.Fig. 3 is the sectional structure chart of the indoor set of the air regulator of the first embodiment.As shown in Figures 2 and 3, the indoor set 100 of the air regulator of present embodiment is provided with front panel 101 in front face side, grid 102 on top side is provided with, in the running of air regulator, front panel 101 is that fulcrum makes upper opening with bottom, by air as shown in arrow F1, F2 from above and above suck, and to spray to the direction of blow-off outlet 103 as shown in arrow F3.Be provided with horizontal wind direction board 104 in the following side of indoor set 100, the blow-off outlet 103 of the air of indoor set 100 can opening and closing by the rotation of horizontal wind direction board 104.
Be close to front panel 101 and above the inner side of grid 102 be provided with the coarse filter 110 being installed on filter frame 111.Possess filter sweeping mechanism 112 in the outside of coarse filter 110, this filter sweeping mechanism 112 moves horizontally on coarse filter 110 while the length direction of indoor set 101 carries out cleaning, thus the dust that the eyelet by filter is caught removing.
In the inner side of coarse filter 110, the indoor heat converter 120 be made up of heat-exchange fin 128 and refrigerant pipe 129 is arranged in the mode of surrounding axial-flow fan 130 as front face side heat exchanger 122, rear side heat exchanger 123 and secondary unit 124.The air of indoor heat converter 120 to the suction inlet suction of machine 100 indoor regulates.The downstream of axial-flow fan 130 heat exchanger disposed in the interior, has multiple fan blade 310.In the present embodiment, axial-flow fan 130 is formed as the fan section 300 be made up of multiple fan blade 310 and demarcation strip 320 axially to link multiple structures as fan section 300a, 300b.The axial-flow fan 130 be made up of multi-disc fan blade 310 configures in the mode clamped by procapsid 131 and back casing 132.Stabilizer 201 and rear guiding piece 202 is formed respectively in the front end of procapsid 131 and back casing 132.
As shown in Figure 3, axial-flow fan 130 is rotated clockwise, and forms the circulation eddy current f20 of the feature as axial-flow fan 130, and goes out by the wind after indoor heat converter 120 as main flow f10 simultaneously, carries out air conditioning.Between adjacent fan blade 310, as flowed into wind f11a, flowing into wind f11b and flowing into as shown in wind f11c, flow into wind direction fan blade 310 to flow into, and as shown in blowout wind f12a, blowout wind f12b and blowout wind f12c, blowout wind sprays from fan blade 310.Blowout wind f22a and the suction wind f21a of blowout near stabilizer 201 form axial-flow fan 130 distinctive circulation eddy current f20 near stabilizer 201.Fan blade 130 produces pressure oscillation at position (hereinafter referred to as " the approach portion ") place close to preceding heat exchanger 122, stabilizer 201 and rear guiding piece 202, and this pressure oscillation becomes main sound source and produces noise.
Fig. 4 is the stereogram of axial-flow fan one section of the indoor set of the air regulator of the first embodiment.Axial-flow fan 130 by installing N sheet fan blade 310 and forming on demarcation strip 320.Fan blade 310 configures in turn from benchmark 330 (due to symmetry, therefore can arbitrarily) inclination predetermined angular.In the present embodiment, angle (hereinafter referred to as " the blade pitgh ") P (n) between the most external diameter point 332 of adjacent fan blade 310 (n is the numbering of the blade of starting at from benchmark) is made to have periodically.
The outer circumference end of fan blade 310 and edge 311 have peak 312a ~ 312d, paddy 313a ~ 313d, are formed through the periodic shape (hereinafter referred to as " waveform ") that level and smooth curve is connected.Now, as described later, there is no change in shape sharply at edge, therefore can not produce the variation of the fluid sharply on edge 311.
At this, in axial-flow fan 130, the contribution of demarcation strip 320 pairs of air blast is little.Therefore, in the present embodiment, at outer circumferential side and edge 311 place of fan blade 310, peak is connected with demarcation strip 320.By the structure making the peak that fan external diameter is large compared with paddy connect with demarcation strip 320, the air quantity reducing amount that demarcation strip 320 causes can be compensated.Therefore, the rotating speed contributed under same air quantity reduces the fan brought and inputs reduction, noise reduction.Further, because the area contacted with demarcation strip 320 increases, the intensity that therefore can also contribute to axial-flow fan 130 improves.
Fig. 5 is the arrangement of the blade pitgh of the fan blade of the axial-flow fan of the indoor set of the air regulator of the first embodiment.The transverse axis of Fig. 5 is fan blade numbering (fan blade becoming benchmark is arbitrary) when fan blade 310 being arranged in turn.The longitudinal axis of Fig. 5 is blade pitgh P (n).Comparative example 1 and comparative example 2 are difference according to fan blade numbering and determine the axial-flow fan 130 of blade pitgh P (n) at random.Comparative example 3 and present embodiment make blade pitgh P (n) periodically increase and decrease the axial-flow fan 130 of (change) according to the order of fan blade numbering.
Fig. 6 is the measurement result of the frequency of the indoor set of the air regulator of comparative example 1 and comparative example 2 and the relation of noise.Comparative example 1 and comparative example 2 are the axial-flow fans 130 determined at random by blade pitgh P (n).The edge of the fan blade 310 of comparative example 1 is straight line, and the edge of the fan blade 310 of comparative example 2 is the waveform shown in Fig. 4.
The noise of axial-flow fan 130 mainly fan blade 310 near approach portion time produce.Therefore, the noise of axial-flow fan 130 was caused by the cycle of fan blade 310 near approach portion, existed and concentrated on to be multiplied with the sheet number of fan blade 310 by the rotating speed of axial-flow fan 130 value of gained and the tendency of blade passing frequency (hereinafter referred to as " BPF ").The noise that frequency becomes BPF is the sound being equivalent to high pitch for human body, and human body may be made to feel uncomfortable especially.
In comparative example 1, make blade pitgh P (n) random, make thus fan blade 310 near approach portion cycle (fan blade 310 near after approach portion to next fan blade 310 time near approach portion) at random.According to the axial-flow fan 130 of comparative example 1, the frequency dispersion of the noise in axial-flow fan 130 can be made.
But in comparative example 1, as shown in Figure 6, result exists multiple randomly at low frequency region (frequency is the region of below BPF) peak value.This is because comparative example 1 fan blade 310 is random near the cycle (fan blade 310 near after approach portion to next fan blade 310 time near approach portion) of approach portion, is applied to the pressure cause jumpy in fan blade 310 when therefore fan blade 310 sequentially passes through approach portion.
At this, first, as comparative example 2, make the edge of fan blade 310 be formed as waveform, attempt thus and relax fan blade 310 and be applied to pressure oscillation in fan blade 310 when sequentially passing through approach portion.
But due to when fan blade 310 sequentially passes through approach portion, the change of the pressure at approach portion place sharply, even if therefore result is that the edge of fan blade 310 is formed as waveform, also almost cannot suppress pressure oscillation.Therefore, as shown in Figure 6, comparative example 2 becomes following result: do not find in noise, to there is large difference with comparative example 1, and input does not reduce yet compared with comparative example 1.
Fig. 7 is the measurement result of the frequency of the indoor set of the air regulator of comparative example 1 and comparative example 3 and the relation of noise.Comparative example 3 is the axial-flow fans 130 blade pitgh P (n) periodically being increased and decreased according to the order of fan blade numbering.Comparative example 1 is the axial-flow fan 130 determining blade pitgh P (n) randomly.The edge of the fan blade 310 of comparative example 3 and comparative example 1 is all straight line.
In comparative example 3, by making blade pitgh P (n) periodically increase and decrease, thus the noise in axial-flow fan 130 can be suppressed to a certain degree to concentrate on the phenomenon of BPF, making fan blade 310 change smoothly near the cycle of approach portion simultaneously.So as a result, the axial-flow fan 130 of comparative example 3 is compared with the comparative example 1 of change at random, the pressure oscillation at approach portion place can be suppressed, thus make the noise reduction of low frequency region.Have periodically by making blade pitgh P (n), the change of blade pitgh P (n) adjacent thus becomes level and smooth, and also become level and smooth from flowing into wind f11a to the change of the adjacent inflow wind of f11c and from blowout wind f12a to the change of f12c in Fig. 3, and fan blade 310 also becomes level and smooth respectively by applied pressure variation during approach portion.
But in comparative example 3, as shown in Figure 7, become following result: compared with comparative example 1, frequency becomes the noise of BPF up to 45dB.In the axial-flow fan 130 of comparative example 3, fan blade 310 is increased and decreased near the cycle of approach portion.But fan blade 310 is not only caused by a slice fan blade 310 near the pressure (wind speed) caused by approach portion, such as, also by the impact of fan blade 310 of front and back, therefore with fan blade 310 near approach portion cycle compared with, change little.That is, in comparative example 3, although make blade pitgh P (n) increase and decrease, and make compared with blade pitgh P (n) comparative example 1 jumpy, it is little that result is that frequency becomes the reduction effect of the noise of BPF.
Fig. 8 is the measurement result of the frequency of the indoor set of the air regulator of the first embodiment and comparative example 3 and the relation of noise.The edge of the fan blade 310 of comparative example 3 is linearity, on the other hand, in the present embodiment, makes the shape of fan blade 310 for the waveform shown in Fig. 4.Present embodiment is same with comparative example 3 is the axial-flow fan 130 that the order of numbering according to fan blade makes blade pitgh P (n) periodically increase and decrease.As shown in Figure 8, in the present embodiment, result is the noise that frequency becomes BPF is about 40dB, reduces 5dB compared with comparative example 3.
Fig. 9 is the Numerical results of the instantaneous value of pressure distribution in the stabilizer of comparative example 3.Figure 10 is the Numerical results of the instantaneous value of pressure distribution in the stabilizer of the first embodiment.Fig. 9 and Figure 10 is by represented by dashed line for the contour of the pressure distribution of axial-flow fan 130 side of stabilizer 201.Figure 11 is the key diagram of the flowing close to the wind speed in fan blade during stabilizer that the first embodiment is described.The benchmark of pressure is atmospheric pressure.
As shown in Figure 9, in comparative example 3, become fan blade 310 pressure step-down partly near the lower end (connecting portion be connected with procapsid 131) of stabilizer 201, and more more increase such distribution toward the lower end side pressure of stabilizer 201.This means to become large pressure oscillation and large sound source, and the input of axial-flow fan 130 increases.In addition, the contour of the pressure distribution of comparative example 3 becomes the straight line with the sides aligned parallel of fan blade 310.
On the other hand, as shown in Figure 10, in the present embodiment, compared with comparative example 1, about pressure increase 10Pa can be made at the lower end of stabilizer 201.As shown in figure 11, by making the edge 311 of fan blade 310 be waveform, thus when fan blade 310 is passed through near stabilizer 201, produced the flowing sucked by adipping towards the paddy 313 wider with the gap between stabilizer 201 by the wind near the peak 312 narrow with the gap between stabilizer 201.That is, present embodiment can form the route of retreat of the wind by narrow space, gap, compared with comparative example 1, can make pressure increase at the lower end of stabilizer 201.
In the present embodiment, as shown in Figure 10, be subject to the impact that edge 311 is waveform, and make pressure contour become waveform.Pressure contour according to Figure 10 is that the phenomenon of waveform is also known, when fan blade 310 is passed through near stabilizer 201, produced the flowing sucked by adipping towards the paddy 313 wider with the gap between stabilizer 201 by the wind near the peak 312 narrow with the gap between stabilizer 201.
It should be noted that, the pressure oscillation of fan blade 310 close to the fan blade 310 during stabilizer 201 is illustrated, but for fan blade 310 and other approach portion and preceding heat exchanger 122 and rear guiding piece 202 close to time fan blade 310 pressure oscillation for, also produce same pressure oscillation.Therefore, according to the present embodiment, by making the edge 311 of fan blade 310 be waveform, the noise that the frequency produced near approach portion becomes BPF can be reduced in thus.
Present embodiment is by the diffusion of the VELOCITY DISTRIBUTION of incline direction, the torque to fan blade 310 that microcosmic is observed also is disperseed, and then the variation of this torque is changed smoothly, therefore to the load reduction of fan blade 310, the power also contributing to axial-flow fan 130 reduces.
It should be noted that, in fan blade 310 not close to the position of preceding heat exchanger 122, stabilizer 201 and rear guiding piece 202, become and be approximately perpendicular to flowing same on the direction at edge 311.
As described above, in the present embodiment, blade pitgh P (n) is changed in the mode becoming periodic function, and make the edge 311 of fan blade 310 be waveform, thus compared with comparative example 1 and comparative example 3, input can be made, overall noise all reduces in whole air quantity region.Such as, under standard (centre) air quantity of specification limit, input can be made to reduce-3%, make overall noise reduction-1dB.
It should be noted that, the atomic little dust less than the filter grid of coarse filter 110 is attached in fan blade 310 by indoor heat converter 120 sometimes.When using all the year round, there is dust and be attached on edge 311 and make the tendency that the spatter property as air regulator reduces.In the rough situation of change, easily produce the disorder of flowing.When the movement disorder of the wind in fan blade 310, form multiple little eddy current.In this case, dust circulates in eddy current, thus the possibility be attached on the wall of fan blade 310 improves.Further, the change of the flowing of the wind in fan blade 310 sharply, dust cannot follow the change of the flowing of wind sharply, thus the possibility be attached on the wall of fan blade 310 improves.In the present embodiment, because the edge 311 of fan blade 310 is wavy, therefore the wind speed at edge 311 place produces distribution, can suppress the generation of eddy current.And, by being formed as wavy, thus make the speed change of its wind speed and direction transformation smoother, therefore can also suppress the change sharply of the flowing of the wind in fan blade 310.Consequently, when using all the year round, present embodiment is compared with comparative example 1, and the dust of attachment can reduce 10%.Therefore, axial-flow fan 130 according to the present embodiment, can also contribute to the raising of spatter property.
Especially because the peak of wave shape and paddy are made up of level and smooth curve, the wind of therefore above-mentioned incline direction is also changed by large curvature smoothly in the apex portion of Feng Hegu, therefore lose, load is low, and contribute to above-mentioned input reduction, noise reduction and spatter property and improve.
In addition, the waveform at the edge 311 of fan blade 310 can also be made up of the complete cycle, but in the tool vicissitudinous cycle, can avoid the increase etc. of the special frequency noise easily produced in the complete cycle, therefore preferably.Such as, expecting that the ratio of Ce Yugu side, peak is more than 1 to 1, such as, is the degree of 1 to 2.The waveform at the edge 311 of fan blade 310 also comprises the situation comprising the tool vicissitudinous cycle.
Blade pitgh P (n) can be in complete period pitch 401, but there is the tendency that special frequency rises due to the blade pitgh P (n) of complete mediation, therefore preferably staggers.And be fixing if stagger, then harmonicity rises and makes noise become large, therefore preferably staggers at random.The situation making blade pitgh P (n) be periodic function comprises situation about staggering a little from periodic function.
The cycle of blade pitgh P (n) is fewer, and the noise under low frequency region more can reduce, but the noise under BPF exists the tendency risen.On the other hand, the cycle of the waveform at the edge 311 of fan blade 310 is fewer, the air quantity flowed from each peak 312 towards paddy 313 more increases, the reduction effect of the noise under BPF is larger, but because the number of peak 312 and paddy 313 reduces, therefore correspondingly suppress the reason of noise under low frequency region and the effect of eddy current to reduce.
That is, expect to consider the noise under low frequency region and the noise under BPF, and based on cycle of blade pitgh P (n), decide the cycle of the waveform at the edge 311 of fan blade 310.In the present embodiment, make blade pitgh P (n) be 2 cycles as shown in Figure 5, and make the edge 311 of fan blade 310 be 3 cycles as shown in Figure 4.Cycle of the waveform at the edge 311 of preferred fan blade 310 carries out the increase and decrease in the scope about 2 periodic quantities relative to the cycle of blade pitgh P (n).In other words, expect the number of peak in the waveform at the edge 311 of fan blade 310 or paddy to be in for the cycle of blade pitgh P (n) ± scope of 2 in.
In addition, although the embodiment that the distance showing peak 312 and paddy 313 is fixing, be not limited to this, also can be formed as the structure same with the change in blade pitgh P (n).If the scope of the size of the change in cycle is within 2 times, then can obtain the effect same with during blade pitgh P (n).That is, if the cycle of blade pitgh P (n) is many, then wind cannot follow the change of edge shape or the change of spacing.In addition, if the cycle of blade pitgh P (n) is few, then edge 311 makes pressure oscillation or speed fluctuation increase close to straight line, thus causes input, noise, dust attachment to worsen.
When the change of blade pitgh P (n) was less than for 1 cycle, from the N number of return to the 1st fan blade time, blade pitgh P (n) sharply changes, and causes wind disorderly.In addition, when being changed to more than 6 cycles of blade pitgh P (n), the change of adjacent blade pitgh P (n) becomes sharply, causes wind disorderly.Therefore, that expects blade pitgh P (n) is changed to 1 cycle more than and (cycle less than 6 cycles) below 5 cycles.
And in the present embodiment, as shown in Figure 5, the sinusoidal mode becoming 2 periodic quantities with the change of blade pitgh P (n) configures fan blade.When blade pitgh P (n) be changed to for 2 cycle, in the main flow f10 of Fig. 3, the spacing of the fan blade 310 that can make the fan blade 310 of the suction side being positioned at main flow f10 and be positioned at blowout side is close.
Such as, when blade pitgh P (n) be changed to for 2 cycle, when blade pitgh P (n) between the most external diameter point 332 of the adjacent fan blade 310 in suction side is narrow, the blade pitgh P (n) that namely position of 180 degree of staggering blows out side is also narrow.Further, when the blade pitgh P (n) of suction side is wide, the blade pitgh P (n) that namely position of 180 degree of staggering blows out side is also wide.That is, the blade pitgh P (n) of the suction side of axial-flow fan 130 and blowout side can be made close, suction side can be reduced and change with the pressure of blowout side, make noise, loss reduction.
In addition, when 3 cycle, the flow field of axial-flow fan 130 is divided into suction, sprays, adds these three regions of circulation eddy current, therefore contributes to input and reduces.
The amplitude a of the blade pitgh P (n) shown in preferred Fig. 5 is different from amplitude b.The difference of preferred amplitude a and amplitude b is more than 0, and is less than 1/10 of average headway 360/N.
Blade pitgh P (n) is periodically, but also can as shown in Figure 5, and the benchmark 401 of complete period assignment when being 2 π/N from average angle staggers predetermined angular dP (n).Even if stagger predetermined angular dP (n), the change of blade pitgh P (n) is also level and smooth, can improve the efficiency of axial-flow fan 130 equally.That is, the mode being not limited to make blade pitgh P (n) to become complete periodic function as sine curve or cosine curve configures the situation of fan blade 310.When the changing of the relative positions of the n-th blade is set to predetermined angular dP (n), expect predetermined angular dP (n) be more than 0 and for average blade pitch 360/N less than 1/20.But, if the change of adjacent blade pitgh P (n) is unsmooth, then there is no effect.As level and smooth scope, expect the difference of adjacent blade pitgh P (n) be average blade pitch and 360/N more than 1/20 and less than 1/3.
As shown in Figure 5, show the embodiment that the straight line 313 that links peak is fixing with the difference dL of the straight line 314 linking paddy, but be not limited to this, the size of dL can Feng Hegu repeatedly time gradually change.The scope of the change of size is within 2 times.Effect is now same with the change in the cycle of blade pitgh P (n), and the noise that complete cycle can be avoided to cause increases, and contributes to noise reduction.
(the second embodiment)
In the present embodiment, the explanation to the inscape same with the first embodiment is omitted.Figure 12 is the key diagram of the flowing close to the wind speed in fan blade during stabilizer that the second embodiment is described.In the first embodiment, the situation that the edge 311 of fan blade 310 is waveform is illustrated, but in the present embodiment, as shown in figure 12, make the shape at the edge 311 of fan blade 310 be the saw shape (zigzag) with multiple leg-of-mutton projection.
In the present embodiment, also can form the route of retreat of the wind by narrow space, gap, and pressure increase can be made at the lower end of stabilizer 201, the noise that frequency becomes BPF can be reduced.
Present embodiment is by the diffusion of the VELOCITY DISTRIBUTION of incline direction, the torque to fan blade 310 that microcosmic is observed also is disperseed, and then the variation of this torque is changed smoothly, therefore to the load reduction of fan blade 310, the power also contributing to axial-flow fan 130 reduces.
(the 3rd embodiment)
In the present embodiment, the explanation to the inscape same with the first embodiment is omitted.Figure 13 is the key diagram of the flowing close to the wind speed in fan blade during stabilizer that the 3rd embodiment is described.In the first embodiment, the situation that the edge 311 of fan blade 310 is waveform is illustrated, but in the present embodiment, as shown in figure 13, make the shape at the edge 311 of fan blade 310 be the saw shape (zigzag) with multiple leg-of-mutton projection.
In the present embodiment, also can form the route of retreat of the wind by narrow space, gap, and pressure increase can be made at the lower end of stabilizer 201, the noise that frequency becomes BPF can be reduced.
Present embodiment is by the diffusion of the VELOCITY DISTRIBUTION of incline direction, the torque to fan blade 310 that microcosmic is observed also is disperseed, and then the variation of this torque is changed smoothly, therefore to the load reduction of fan blade 310, the power also contributing to axial-flow fan 130 reduces.
Claims (6)
1. an indoor set for air regulator, is characterized in that, possesses:
Indoor heat converter;
Axial-flow fan, it is arranged on the downstream of described indoor heat converter, has multiple fan blade that outer diameter shape is waveform or saw shape,
Described fan blade with the blade pitgh approximate period property of described axial-flow fan the mode that increases and decreases arrange.
2. the indoor set of air regulator according to claim 1, is characterized in that,
The increase and decrease of the blade pitgh of described axial-flow fan is the approximate period function in 1 cycle in cycle to 5.
3. the indoor set of air regulator according to claim 2, is characterized in that,
The increase and decrease of the blade pitgh of described axial-flow fan is the approximate period function in 2 cycles or 4 cycles.
4. the indoor set of air regulator according to claim 2, is characterized in that,
The outer diameter shape of described fan blade is waveform or the saw shape with multiple peak or multiple paddy,
The number of described peak or described paddy be in relative to described axial-flow fan blade pitgh cycle ± 2 scope in.
5. the indoor set of air regulator according to claim 1, is characterized in that,
Described axial-flow fan possesses the demarcation strip installing described fan blade,
The outer diameter shape of described fan blade is waveform or the saw shape with multiple peak,
Described peak connects with described demarcation strip.
6. an air regulator, is characterized in that, possesses:
The indoor set of the air regulator according to any one of claim 1 to claim 5;
There is the off-premises station of compressor, expansion mechanism and outdoor heat converter.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013184598A JP6601994B2 (en) | 2013-09-06 | 2013-09-06 | Indoor unit of air conditioner and air conditioner using the same |
| JP2013-184598 | 2013-09-06 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104422029A true CN104422029A (en) | 2015-03-18 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410389250.9A Pending CN104422029A (en) | 2013-09-06 | 2014-08-08 | Air conditioner indoor unit and air conditioner using the indoor unit |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6601994B2 (en) |
| CN (1) | CN104422029A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110878761A (en) * | 2019-12-06 | 2020-03-13 | 宁波奥克斯电气股份有限公司 | Cross-flow fan blade and air conditioner |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107289514B (en) * | 2017-05-27 | 2019-11-05 | 青岛海尔空调器有限总公司 | Air conditioner room unit and its out wind pendulum leaf |
| CN109555724B (en) * | 2017-09-26 | 2021-02-02 | 青岛海尔智慧厨房电器有限公司 | Staggered tooth impeller and range hood |
| KR101894206B1 (en) * | 2018-04-04 | 2018-08-31 | 서울대학교산학협력단 | Cross Flow Fan and Housing |
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| JP3137897B2 (en) * | 1996-03-12 | 2001-02-26 | 株式会社日立製作所 | Once-through fan |
| JP3995010B2 (en) * | 2005-09-28 | 2007-10-24 | ダイキン工業株式会社 | Impeller of multiblade blower and method of manufacturing the same |
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| JPS4992507U (en) * | 1972-11-30 | 1974-08-10 | ||
| JPH0874783A (en) * | 1994-09-06 | 1996-03-19 | Toshiba Corp | Multiblade rotary body |
| CN1164619A (en) * | 1996-01-18 | 1997-11-12 | 三菱电机株式会社 | DC blasting vane wheel |
| CN1270102C (en) * | 1998-03-30 | 2006-08-16 | 三洋电机株式会社 | Cross-flow fan and air-conditioner using it |
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| CN110878761A (en) * | 2019-12-06 | 2020-03-13 | 宁波奥克斯电气股份有限公司 | Cross-flow fan blade and air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6601994B2 (en) | 2019-11-06 |
| JP2015052279A (en) | 2015-03-19 |
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| Date | Code | Title | Description |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C41 | Transfer of patent application or patent right or utility model | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20160825 Address after: Hongkong aoteng Plaza No. 8 Chinese Kowloon Linze street 12 floor Applicant after: Johnson Controls Hitachi air conditioning technology (Hongkong) Co., Ltd. Address before: Tokyo, Japan Applicant before: Hitachi Appliances Inc. |
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| TA01 | Transfer of patent application right | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20180702 Address after: Tokyo, Japan, Japan Applicant after: Hitachi Johnson Controls Air Conditioning Co., Ltd. Address before: Hongkong aoteng Plaza No. 8 Chinese Kowloon Linze street 12 floor Applicant before: Johnson Controls Hitachi air conditioning technology (Hongkong) Co., Ltd. |
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| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20150318 |