CN103097821B - The pressure fan of outdoor unit, outdoor unit and freezing cycle device - Google Patents

The pressure fan of outdoor unit, outdoor unit and freezing cycle device Download PDF

Info

Publication number
CN103097821B
CN103097821B CN201080069087.8A CN201080069087A CN103097821B CN 103097821 B CN103097821 B CN 103097821B CN 201080069087 A CN201080069087 A CN 201080069087A CN 103097821 B CN103097821 B CN 103097821B
Authority
CN
China
Prior art keywords
fan
mentioned
outdoor unit
propeller type
rotating shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN201080069087.8A
Other languages
Chinese (zh)
Other versions
CN103097821A (en
Inventor
冈泽宏树
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of CN103097821A publication Critical patent/CN103097821A/en
Application granted granted Critical
Publication of CN103097821B publication Critical patent/CN103097821B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/38—Fan details of outdoor units, e.g. bell-mouth shaped inlets or fan mountings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
    • F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation

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)
  • Other Air-Conditioning Systems (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)

Abstract

The invention provides the outdoor unit etc. of the freezing cycle device with the pressure fan that noise, electric power can be suppressed to increase.Pressure fan has propeller type fan (1) to rotate centered by the rotating shaft of vertical and horn mouth (2).Horn mouth (2), along the direction of rotation of the blade of propeller type fan (1), forms wall in the outside of the outer circumference end of blade, for gas rectification.The wall as inclined-plane that the wind path that horn mouth (2) has blowout side is formed with expanding, and be the shape meeting following relation as condition: the length H on the rotating shaft direction of the suction side on inclined-plane and the terminal room of blowout side and the fan diameter D of propeller type fan (1) is the relation of H/D>=0.04; Connect the relation that the straight line of two terminals on inclined-plane and the angle θ of rotating shaft are 0< θ≤60 °; The length L of the blade of the length L the rotating shaft direction of the suction side terminal part from the opening portion of suction side to inclined-plane and the axial propeller type fan of rotation (1) 0, be L/L 0the relation of>=0.5.

Description

The pressure fan of outdoor unit, outdoor unit and freezing cycle device
Technical field
The present invention relates to the outdoor unit etc. with pressure fan, above-mentioned pressure fan has propeller type fan and horn mouth.
Background technology
There is the propeller type fan making to have blade (screw) rotate and produce air flowing and to carry out blowing the pressure fan (fan unit) of (cooling, heat radiation etc.).This pressure fan with propeller type fan is widely used in the fields such as the cooling device of the outdoor unit (off-premises station), refrigerator, ventilation fan, computer etc. of refrigerating air-conditioning.
In this pressure fan, such as, there is the horn mouth of the direction of rotation formation wall along propeller type fan.This bell-mouthed opening portion majority expands, successfully to carry out the blowout (for example, see patent document 1,2) of air.
At first technical literature
Patent document 1: Japanese Patent No. 3087876 publications
Patent document 2: Japanese Patent No. 3199931 publications
Summary of the invention
The problem that invention will solve
Such as, in above-mentioned pressure fan, just merely expanded opening portion, then the sound becoming noise increases, and fan efficiency reduces.Such as, when using in the outdoor unit above-mentioned pressure fan being arranged on aircondition, the noise that unit produces outdoor because of the rotation of propeller type fan can harass neighbouring resident.Therefore, the low noise of outdoor unit is required.On the other hand, in recent years, in order to prevent earth environment warmization, the energy-saving of aircondition is also required.In order to realize energy-saving, the air quantity increased in outdoor unit is effective measures.But substantially, along with the increase of air quantity, noise also increases.In addition, in aircondition etc., be mostly do not shut down or the duration of runs very long, so the power reducing of pressure fan self is also very important.
For this reason, the object of the invention is to obtain have suppress noise, the outdoor unit etc. of freezing cycle device of the pressure fan that suppresses electric power to increase.
Solve the technical scheme of problem
The pressure fan of outdoor unit of the present invention, has propeller type fan and horn mouth, and above-mentioned propeller type fan to rotate and to have multiple blades of the flowing of the gas producing the direction contrary with gravity direction centered by the rotating shaft of gravity direction; Above-mentioned horn mouth, along the direction of rotation of the blade of propeller type fan, forms the wall of annular, for carrying out rectification to gas in the outside of the outer circumference end of blade; The wall as inclined-plane that the wind path that this horn mouth has blowout side is formed with expanding, and be the shape meeting following relation as condition: the length H on the rotating shaft direction between the suction side on inclined-plane and the terminal of blowout side and the fan diameter D of propeller type fan is the relation of H/D>=0.04; Connect the relation that the straight line of two terminals on inclined-plane and rotating shaft angulation θ are 0< θ≤60 °; And the length L of the length L the rotating shaft direction of suction side terminal part from the opening portion of suction side to inclined-plane and the propeller type fan blade on rotating shaft direction 0, be L/L 0the relation of>=0.5.
The effect of invention
In the pressure fan of outdoor unit of the present invention, constitute the pressure fan forming following bell-mouthed outdoor unit, the inclined-plane that the wind path that this horn mouth has blowout side is formed with expanding, and relative to propeller type fan to meet L/L 0>=0.5, the shape of the relation of 0< θ≤60 °, H/D>=0.04 is formed.So, fan diameter need not be increased, just can make the static pressure of open sides and the static pressure of the relation of air quantity close to surge area and the relation of air quantity, such as, the ratio sound level (at operating point place when maximum quantity of wind drives is Bi Uproar sound), fan efficiency reduces with the minimum difference than sound level, maximum fan efficiency, like this, the input of fan can be reduced, realize low noise.
Accompanying drawing explanation
Fig. 1 is the figure of the summary of the pressure fan representing embodiment of the present invention 1.
Fig. 2 is the P-Q characteristic and the K that represent propeller type fan 1 monomer sthe figure of-Q characteristic.
Fig. 3 represents the P-Q characteristic of propeller type fan 1 monomer and the figure of η-Q characteristic.
Fig. 4 represents P-Q characteristic and K sthe figure of the relation of-Q characteristic and diameter.
Fig. 5 is the figure of the relation representing P-Q characteristic and η-Q characteristic and diameter.
Fig. 6 is the figure of one of dimensional parameters representing horn mouth 2 example.
Fig. 7 is the figure of the P-Q characteristic represented in dimensional parameters.
Fig. 8 represents to make L/L 0the figure of P-Q characteristic during change.
Fig. 9 represents air quantity Q 2time than sound level K swith L/L 0the figure of relation of value.
Figure 10 is the figure of the P-Q characteristic represented when rake angle θ is changed.
Figure 11 represents air quantity Q 2fan efficiency η, than sound level K swith the figure of the relation of angle θ.
Figure 12 is the figure of P-Q characteristic when representing the value change making H/D.
Figure 13 represents air quantity Q 2time the figure of relation of value of static pressure P and H/D.
Figure 14 represents air quantity Q 2fan efficiency η, than sound level K swith the figure of the relation of H/D.
Figure 15 is the stereogram of other shape representing horn mouth 2.
Figure 16 is the figure of other shape example representing rake 5a.
Figure 17 is the figure of the structure representing upward type outdoor unit.
Figure 18 is the figure of the structure representing transverse-blow type outdoor unit.
Figure 19 is the bell-mouthed exploded perspective view of transverse-blow type.
Figure 20 is the figure representing the relation that the shape of horn mouth 2 and air flow.
Figure 21 is the shape of the horn mouth 2 representing embodiment 2 and the figure of air flowing.
Figure 22 is the figure of the relation representing horn mouth 2 and fan protection part.
Figure 23 is the figure of relation representing fan input, noise and angle [alpha].
Figure 24 is the figure of the propeller type fan 1 representing embodiment 4.
Figure 25 is the figure of the flow trace line of the wing tip vortex represented when not having rib 6.
Figure 26 is the figure of the flow trace line of wing tip vortex when indicating rib 6.
Figure 27 is the figure in the suction opening portion 3 representing horn mouth 2.
Figure 28 is the figure of the relation representing P-Q characteristic and R/D value.
Figure 29 represents air quantity Q 2in than sound level K swith the figure of the relation of R/D value.
Figure 30 represents air quantity Q 2in the figure of relation that is worth of fan efficiency η and R/D.
Figure 31 is the pie graph of the refrigerating air-conditioning of embodiment of the present invention 6.
Detailed description of the invention
Embodiment 1
Fig. 1 is the figure of the summary of the pressure fan representing embodiment of the present invention 1.In FIG, the profile of propeller type fan 1 and horn mouth 2 is represented.The pressure fan of present embodiment is such as arranged in the outdoor unit of the freezing cycle device of aircondition etc.
Propeller type fan 1 is that multiple blade (propeller blade, the wing) rotates and produces the tube-axial fan that air (fluid) flows centered by rotating shaft under the driving of the (not shown) such as motor of energising.Here the propeller type fan 1 illustrated is the fan of advance wing-like, but is not particularly limited to this.In addition, in outdoor unit, by propeller type fan 1(pressure fan) be configured to, rotating shaft is roughly along gravity direction (vertical, below sometimes also referred to as the short transverse of pressure fan), upward type pressure fan towards the direction blow out air contrary with gravity direction.
Horn mouth 2 is covered with propeller type fan 1(along the circumferential direction (direction of rotation) of propeller type fan 1 and surrounds propeller type fan 1 around), rectification is carried out to the air flowing that the rotation of propeller type fan 1 produces.Therefore, around propeller type fan 1, define the wall of circular tube shaped.As shown in Figure 1, the horn mouth 2 of present embodiment is covered with roughly 50% of the rotating shaft direction (short transverse) of propeller type fan 1.
Suction opening portion 3 is for sucking the part of air and opening at the upstream side (suction side) of horn mouth 2.In the horn mouth 2 of present embodiment, distance (diameter of opening portion) between the rotating shaft of propeller type fan 1 and the terminal part in suction opening portion 3, than the distance (diameter of straight sections 4) between rotating shaft and the face of straight sections 4 long (suction opening portion 3 terminal has extension part).Internal face (with propeller type fan 1 face in opposite directions) from the suction side terminal part of straight sections 4 to suction opening portion 3 terminal is flexure plane (section shape is circular arc).Flexure plane has radius of curvature R, and the curved surface portion in suction opening portion 3 is called fillet part 3a.
Straight sections 4 is the internal face of horn mouth 2 parts parallel with the rotating shaft of propeller type fan 1.In the short transverse of pressure fan, the position of blowout lateral terminal part of straight sections 4 is roughly the same with the position of the blade of the blowout side of propeller type fan 1, but is not particularly limited to this.
Blowout opening portion 5 be in the downstream (blowout side) of horn mouth 2 for blow out air the part of opening.In blowout opening portion 5 similarly, the distance (diameter of opening portion) between the rotating shaft of propeller type fan 1 and the terminal part of blowout opening portion 5 is longer than the distance (diameter of straight sections 4) between rotating shaft and the face of straight sections 4.Further, the internal face blowing out lateral terminal from the blowout lateral terminal (blowout suction side, opening portion 5 terminal) of straight sections 4 to blowout opening portion 5 is the inclined-plane with extension part, and section shape is formed as taper (horn-like).The part of this taper is called rake 5a.Here, the horn mouth 2 of present embodiment has straight sections 4, but, also can form internal face with rake 5a and fillet part 3a.
Fig. 2 is the P-Q characteristic and the K that represent propeller type fan 1 monomer sthe figure of-Q characteristic.Fig. 3 represents the P-Q characteristic of propeller type fan 1 monomer and the figure of η-Q characteristic.Here, P represents static pressure, and Q represents air quantity, K srepresent than sound level [dB], η represents fan efficiency (static pressure efficiency) [%].In addition, than sound level K sand fan efficiency η and static pressure P and air quantity Q is the relation meeting following formula (1), (2).In formula, SPL represents the noise [dB] apart from propeller type fan 1 preset distance position, and T represents moment of torsion [Nm], and ω represents angular speed [rad/s].In addition, the unit of the static pressure P1 in (1) formula is [mmAq], air quantity Q 1unit be [m 3/ min].On the other hand, the static pressure P in (2) formula 2unit be [Pa], air quantity Q 1unit be [m 3/ s].
K S=SPL-10log 10（P 1·Q 1 2.5）…（1）
η=100×P 2·Q 2/Tω…（2）
Below, with reference to Fig. 2 and Fig. 3, static pressure P, air quantity Q are described, than sound level K s, fan efficiency η relation.P-Q characteristic is the characteristic representing the relation of setting the rotation speed of the fan of propeller type fan 1 as flowing resistance time constant and static pressure P and air quantity Q.Here, low air quantity, high static pressure side are called closed side, high air quantity, low static pressure side are called open sides.Usually, flowing resistance is less, and wind more easily flows (static pressure P is lower, and air quantity Q is larger); Flowing resistance is larger, and wind is more not easy to flow (static pressure P is higher, and air quantity is fewer).
But, always not there is such relation between air quantity Q and static pressure P, the region that the change that also there is static pressure P reduces relative to air quantity Q.This region is called surge area, when any propeller type fan 1 rotates, near surge area, is all than sound level K sminimum and fan efficiency η is maximum.
Fig. 4 represents P-Q characteristic and K sthe figure of the relation of the fan diameter (fan rotating diameter) of-Q characteristic and propeller type fan 1.Fig. 5 is the figure of the relation of the diameter representing P-Q characteristic and η-Q characteristic and propeller type fan 1.As shown in Figure 4 and Figure 5, when being strengthened by fan diameter, surge area is moved to open sides.In addition, if strengthen fan diameter, then the gradient of P-Q characteristic is less than surge area in open sides region; Otherwise if reduce fan diameter, then the gradient of P-Q characteristic is larger than surge area in open sides region.
Below, operating point is described.There is propeller type fan 1(pressure fan) aircondition outdoor unit in, if predetermined wind amount Q 0time the rotation speed of the fan of propeller type fan 1 be N 0.From rotation speed of the fan N 0time the P-Q characteristic of monomer of propeller type fan 1, obtaining air quantity is Q 0time static pressure P 0, (P 0, Q 0) as operating point.
In pressure fan, when operating point is positioned at open sides than surge area, operating point place than sound level K slarger than the ratio sound level in sound level point than minimum; Fan efficiency η is less than the fan efficiency in maximum fan efficiency point.At this moment, if strengthen fan diameter, then surge area is moved to open sides as previously mentioned, close to operating point, so, operating point place than sound level K s, fan efficiency η close to minimum than the fan efficiency in the ratio sound level in sound level point, maximum fan efficiency point, can suppress noise, suppress fan input (electric power supply).
But if strengthen fan diameter, then the size of pressure fan also becomes large.Thus the machine dimensions of installing pressure fan also must strengthen.Therefore, size increase brings the problems such as cost raising, aesthetic appearance reduction, installation space increase.
For this reason, when not strengthening fan diameter, operating point is positioned at open sides than surge area, in order to make operating point place than sound level K s, fan efficiency η than sound level, maximum fan efficiency, makes the gradient of P-Q characteristic reduce in open sides region is than surge area close to minimum, strengthens the static pressure of open sides.At this moment, K sthe gradient of-Q characteristic, η-Q characteristic also diminishes, compared with time large with gradient, due to operating point place than sound level K s, fan efficiency η deviates from minimizing with the minimum fan efficiency than the ratio sound level of sound level point, maximum fan efficiency point, so, noise can be suppressed, suppress fan input.In addition, at K swhen the gradient of-Q characteristic, η-Q characteristic is little, even if when such as changing the air quantity setting etc. of pressure fan and cause operating point to change, also can reduce than sound level K s, fan efficiency η change, so, can high efficiency running be carried out.Here, the minimum impact being mainly subject to fan diameter than sound level, maximum fan efficiency.Fan diameter is larger, minimum less than sound level, and maximum fan efficiency is larger; Fan diameter is less, minimum larger than sound level, and maximum fan efficiency is less.In addition, have following features: fan diameter is larger, the gradient of P-Q characteristic is less; Fan diameter is less, and the gradient of P-Q characteristic is larger.
Such as, in the aircondition with propeller type fan 1, sometimes air quantity is set as multistage change.When fan diameter can not be strengthened, at K sin-Q characteristic, η-Q characteristic, operating point during maximum quantity of wind running deviates from than sound level point, maximum fan efficiency point with minimum, easily increases noise and fan input.This is because as mentioned above, when fan diameter fully can not be strengthened, surge area be positioned at closed side and maximum quantity of wind running time operating point be positioned at the cause of open sides.
Fig. 6 is the figure of one of dimensional parameters representing horn mouth 2 example.As shown in Figure 6, if the diameter of propeller type fan 1 (fan diameter) is D.If the blowout lateral terminal part from suction opening portion 3 terminal to straight sections 4, length (horn mouth height) the rotating shaft direction of horn mouth 2 is L, if the length (fan height) of the blade on the rotating shaft direction of propeller type fan 1 is L 0.In addition, if the rake 5a in blowout opening portion 5, be H along the axial length of rotation (highly, hereinafter referred to rake height) of propeller type fan 1, set length (hereinafter referred to rake length) along fan diameter D direction as W.Rake angle θ is set to by forming angulation between the direction of the conical by its shape of rake 5a and the rotating shaft direction of propeller type fan 1.
Fig. 7 is the figure of the P-Q characteristic represented in the dimensional parameters of Fig. 6.Represent D=700mm, L/L in the parameter of the pressure fan shown in Fig. 6 0=0.1, H/D=0.01, θ=45 °, rotation speed of the fan are N atime P-Q characteristic.In the figure 7, air quantity Q 1represent the air quantity near surge area, air quantity Q 2represent the air quantity at the operating point place being positioned at open sides than surge area.
The following describes the pressure fan with following structure, wherein, the static pressure P being positioned at the operating point place of open sides than surge area increases, and the gradient being positioned at open sides in P-Q characteristic than surge area diminishes.Open sides described below refers to the operating point being positioned at open sides than surge area.
Fig. 8 represents to make L/L 0the figure of P-Q characteristic when having changed.Here, if fan height L 0for constant, horn mouth height L changed, thus makes L/L 0change.As shown in Figure 8, be Q at air quantity 1surge area near, no matter L/L 0value how, static pressure P is roughly the same.On the other hand, L/L 0be worth larger, then than air quantity Q 1be positioned at the air quantity Q of open sides 2operating point place, work as L/L 0during <0.5, static pressure P increases, and works as L/L 0when>=0.5, static pressure P is roughly the same.
Fig. 9 represents that rotation speed of the fan is N a, air quantity is Q 2time pressure fan in than sound level K s[dB] and L/L 0the figure of the relation of value.As shown in Figure 9, L/L is worked as 0during <0.5, L/L 0value larger, then can realize open sides than sound level K sreduction.On the other hand, L/L is worked as 0when>=0.5, open sides than sound level K ssubstantially constant.
Its reason is, when horn mouth height L is low, in the blade of the propeller type fan 1 do not covered by horn mouth 2, easily produces wing tip vortex, and then produces the noise caused by this wing tip vortex.On the other hand, when horn mouth height L height, for wing tip vortex, stream is narrow, so the noise that wing tip vortex causes reduces, but the static pressure variation on the fan side wall of horn mouth 2 increases.Therefore, L/L is worked as 0during <0.5, L is longer for horn mouth height, and the noise that wing tip vortex causes is lower, and works as L/L 0when>=0.5, both impacts are same degree, not change, so, than sound level K sdo not change.From the foregoing, the relation of the short transverse of propeller type fan 1 and horn mouth 2 is preferably L/L 0>=0.5.
Below, L/L is established in the parameter shown in Fig. 6 0=0.5, W/D=0.15 situation when rake angle θ is changed are described.At this moment, H=W/tan θ.In order to W=0 and fan diameter D large situation difference, if rake length W is constant.
Figure 10 is the figure of the P-Q characteristic represented when setting rotation speed of the fan as NA and rake angle θ is changed.Near surge area, no matter rake angle θ how, and static pressure P is roughly the same.On the other hand, when θ >=60 °, rake angle θ is larger, and the static pressure P being positioned at open sides than surge area is less, and when 0< θ≤60 °, the static pressure P of open sides is roughly the same.
Figure 11 represents that rotation speed of the fan is N a, air quantity is Q 2time fan efficiency η, than sound level K swith the figure of the relation of angle θ.In fig. 11, near surge area, tube angulation θ is not how, fan efficiency η, than sound level K sall roughly the same.But when θ>=60 °, θ is larger, and fan efficiency η is lower, than sound level K slarger.On the other hand, when 0< θ≤60 °, the fan efficiency η of open sides, than sound level K sincrease rate of change little, and think roughly the same (due between 45 ° and 60 ° fan efficiency η, than sound level K sincrease a little, so, more preferably 0< θ≤45 °).
The fan efficiency η of open sides during 0< θ≤60 °, than sound level K sthat owing to blowing out the enlarged areas of the blowout wind path of opening portion 5, thus the speed of the air of blowout reduces, and static pressure P rises than the reason improved during θ>=60 °.In addition, because blowout opening portion 5 has extension part, so blowout wind path plays the effect of diffuser.Now, when 0< θ≤60 °, the air near rake 5a is blown out by along rake 5a, so play the function of diffuser.
Figure 12 represents to set rotation speed of the fan as N aand the figure of P-Q characteristic when H/D value is changed.Figure 13 represents that rotation speed of the fan is N a, air quantity is Q 2time the figure of relation that is worth of static pressure P and H/D.Here, in the parameter of the pressure fan shown in Fig. 6, if L/L 0=0.5, θ=60 °.
As can be seen from Figure 12, near surge area, no matter H/D value how, and static pressure P is roughly the same.On the other hand, more leaning on open sides than surge area, as H/D<0.04, H/D value is larger, then static pressure P is larger.On the other hand, when H/D >=0.04, the static pressure P of open sides is roughly the same.
In addition, as shown in figure 13, H/D value is larger, then the static pressure P of open sides is larger, but, static pressure P relative to the increase of H/D value than little during H/D<0.04.
Figure 14 represents that rotation speed of the fan is N a, air quantity is Q 2time fan efficiency η, than sound level K swith the figure of the relation of H/D.In fig. 14, near surge area, no matter the value of H/D how, fan efficiency η, than sound level K sbe all roughly the same.On the other hand, as H/D<0.04, H/D value is less, and fan efficiency η is lower, than sound level K slarger.And when H/D>=0.04, relative to the increase of H/D value, the fan efficiency η of open sides, than sound level K simprovement effect relatively reduce.
The fan efficiency of open sides during H/D >=0.04 and than the reason improved during H/D<0.04 be than sound level, owing to blowing out the enlarged areas of wind path, thus the speed of blow out air reduces, the cause that static pressure P rises, and owing to blowing out opening portion 5, there is extension part, so blowout wind path plays the effect of diffuser.At this moment, due to H/D >=0.04, so effectively play the function as diffuser.
If fan diameter D is little, then surge area is moved to closed side as mentioned above, so, must guarantee that fan diameter D has predetermined size (such as in outdoor unit, preferably more than 600mm).Therefore, strengthen H/D value if want, will strengthen rake height H, this size along with horn mouth 2 downstream increases.
Such as, as shown in figure 14, during H/D>=0.04, even if the value of H/D increases, the fan efficiency η of open sides, than sound level K simprovement effect also relatively reduce.Therefore, if H/D >=0.04, then such as with the relation of the casing of heat source unit, when still having leeway in the size permissible range of horn mouth 2, strengthen the value of H/D.Otherwise, in situation spaceless, as long as at least guarantee H/D=0.04, the fan efficiency η of open sides just can be improved, than sound level K s.
In the pressure fan of present embodiment being installed on outdoor unit, as mentioned above, to meet H/D>=0.04,0< θ≤60 °, L/L 0the mode of impose a condition (parameter) of the relation of>=0.5 forms propeller type fan 1, horn mouth 2.As shown in above-mentioned each result, if form pressure fan according to imposing a condition of forming of each relation, then can play the effect of the increase suppressing noise, electric power (fan input).Here, such as in each condition to noise, electric power increase inhibition the highest be the situation meeting H/D >=0.04.Then, be 0< θ≤60 °, L/L successively 0the situation of>=0.5.Therefore, even if do not meet whole imposing a condition, impose a condition or its combination as long as meet one, just can obtain effect of the present invention.
Figure 15 is the stereogram of other shape representing horn mouth 2.Such as, here there is following situation, if horn mouth 2(especially blows out opening portion 5) diameter longer than at least one party of the width of outdoor unit casing and depth part, then horn mouth 2 leans out, contact with each other with the horn mouth of other outdoor unit, thus be not easy multiple outdoor unit is closely configured.For this reason, in order to the width and depth part making the length to diameter ratio outdoor unit casing of horn mouth 2 shortens, also its shape can be changed partly.Such as, in the horn mouth 2 of Figure 16, make rake angle θ along all-round be not steady state value, make its local not identical.Like this, horn mouth 2 does not lean out, and meets above-mentioned imposing a condition.
Figure 16 is the figure of other shape example representing rake 5a.Such as, in Fig. 1 etc., it is straight line that rake 5a is formed as its section shape.But, due to manufacture, outward appearance, size restriction etc., also have the situation that can not be formed by straight lines.At this moment, as long as connecting the straight line angulation at rake 5a two ends is roughly 0< θ≤60 °, effect same when just can to obtain with rake 5a be straight line.Such as, the roughly circular shape of the spill shown in Figure 16 (a), the roughly circular shape etc. of the convex shown in Figure 16 (b) can be become.
Figure 17 is the figure of the structure representing upward type outdoor unit.Figure 17 (a) represents that the outdoor heat exchanger carrying out the heat exchange of cold-producing medium and air is configured to the outdoor unit of コ font in casing.Figure 17 (b) represents that outdoor heat exchanger is configured to the outdoor unit of V-shaped, W font.As shown in figure 17, in upward type outdoor unit, in コ font, the multistage bending configuration of V-shaped, W font.Pressure fan is towards direction (blowing up direction) blow out air contrary with gravity direction.
Figure 18 is the figure of the structure representing transverse-blow type outdoor unit.As shown in figure 18, the pressure fan of transverse-blow type outdoor unit is towards the direction blow out air vertical with gravity direction.In transverse-blow type outdoor unit, outdoor heat exchanger is configured to L-shaped.
Here, if the heat exchanger that the L-shaped of the heat exchanger configure the コ font of the upward type shown in Figure 17 (a) and transverse-blow type configures compares, then the heat exchanger of コ font configuration sucks air with 3, and the heat exchanger of L-shaped configuration sucks air with 2.Therefore, the configuration of コ font is than the easy installation volume guaranteeing heat exchanger of L-shaped configuration.
In addition, when the multistage bending configuration of the upward type shown in Figure 17 (b), to every 1 propeller type fan (pressure fan) 1, be in the shape of the letter V configuration heat exchanger.At this moment, identical when configuring with L-shaped, be suck air with 2.In addition, 2 heat exchangers are equal length.On the other hand, when the L-shaped configuration that transverse-blow type outdoor unit is such, the heat exchanger length sucking face is short.Therefore, the V-shaped configuration in upward type outdoor unit is than the easy installation volume guaranteeing heat exchanger of L-shaped configuration.Therefore, the frontal area of heat exchanger increases, and is reduced by speed before heat exchanger, so the flowing resistance of heat exchanger reduces, and the flowing resistance of whole outdoor unit also can reduce.
Below, illustrate as representing that operating point is in closed side or the index at open sides with loss coefficient ξ.If when the static pressure of operating point is P, air quantity is Q, loss coefficient ξ ξ=P/Q 2represent.Here, ξ is less, and operating point is at open sides, and ξ is larger, and operating point is in closed side.
Therefore, as mentioned above, usually, upward type outdoor unit is compared with transverse-blow type outdoor unit, and the flowing resistance of heat exchanger is little, so loss coefficient ξ is little, and operating point is positioned at open sides.In order to make operating point near surge area, the fan diameter D that upward type needs is larger than transverse-blow type.When the design of outdoor unit size can not strengthen fan diameter D by restrictions such as setting area, operating point is positioned at open sides than surge area, than sound level K sincrease, fan efficiency η reduces.
As can be seen here, do not strengthen fan diameter D and make operating point near the structure of the present invention of surge area, compared with transverse-blow type outdoor unit, being that upward type outdoor unit needs more, more can playing its effect.
Below, the horn mouth of upward type and the bell-mouthed difference of transverse-blow type are described.For the horn mouth of upward type, the horn mouth 2 of the such shape of such as Figure 15 can be integrally formed with resin, can not in accordance with the L/L of Fig. 1 0and it is integrally formed.
Figure 19 is the bell-mouthed exploded perspective view of transverse-blow type.In transverse-blow type outdoor unit, normally by integrally formed for the horn mouth metallic plate 10 shown in Figure 19 make bell-mouthed.At this moment, the L/L of horn mouth 2 can not be lengthened 0(such as L/L 0=1), other parts are needed in order to lengthen.
Therefore, difficult for upward type outdoor unit for transverse-blow type outdoor unit ratio for the horn mouth shape with structure of the present invention, so, for transverse-blow type outdoor unit, and impracticable.
As mentioned above, according to the pressure fan of embodiment 1, L/L 0>=0.5,0< θ≤60 °, H/D>=0.04 form the pressure fan of outdoor unit as imposing a condition, so, fan diameter D need not be strengthened, just can make the static pressure P of open sides and the static pressure P of the relation of air quantity Q close to surge area and the relation of air quantity Q, fan efficiency η can be improved, than sound level K s.Therefore, fan input can be reduced and suppress noise.
Embodiment 2
Figure 20 is the figure representing the shape of horn mouth 2 and the relation of air flowing.In fig. 20, the flowing of air is represented with streamline.In horn mouth downstream from the air that blowout opening portion 5 blows out, the closer to the wall of rake 5a, then more along rake 5a towards tilted direction stream.At this moment, such as when building roof is provided with the outdoor unit of multiple stage aircondition, be subject to the attraction of propeller type fan 1 of adjacent outdoor unit, the impact etc. of external wind, likely produce the short circulation that sucked by adjacent outdoor unit of wind towards tilted direction blowout.Such as, in casing, had the outdoor unit of the outdoor heat exchanger of condenser effect, the outdoor unit of air having sucked the high temperature blown out from this outdoor unit, the temperature difference of cold-producing medium and air reduces, heat exchanger effectiveness reduces, and there is the possibility that COP reduces.
Figure 21 represents the shape of horn mouth 2 of embodiment 2 and the figure of the flowing of air.The downstream exit portion (terminal part) of the blowout opening portion 5 of the horn mouth 2 of the present embodiment shown in Figure 21 is straight sections 5b.Here, at rake 5a, meet impose a condition (parameter) in embodiment 1.
In addition, in the downstream of horn mouth 2, the air of outer peripheral portion is along rake 5a, straight sections 5b flowing, and (direction contrary with gravity direction) blows out upward, so, the short circulation flowing to adjacent outdoor unit can be suppressed.
In addition, in order to make foreign matter not enter blowout opening portion 5, protection propeller type fan 1 etc., the cancellate fan protection part covering blowout opening portion 5 is set sometimes.At this moment, by the terminal part in horn mouth downstream is made straight sections 5b, can easily fan attachment guard member.
Like this, according to the outdoor unit of pressure fan with embodiment 2, owing to forming straight sections 5b in downstream outlet (terminal part) of blowout opening portion 5, so, to not bringing the top of impact to send air to adjacent outdoor unit, thus can suppress short circulation.In addition, cancellate fan protection part can easily be fixed.
Embodiment 3
Figure 22 represents the horn mouth 2 of pressure fan and is arranged at the figure of relation of fan protection part of pressure fan.In fig. 22, the cancellate mesh covered blowout opening portion 5 of fan protection part, the machine etc. in protection propeller type fan 1, outdoor unit casing.Here, grid also has length in short transverse.Therefore, due to angle, the air collides of blowout is to side.Here, angle formed by the grid of fan protection part and fan rotation axis is α.
Figure 23 is the figure of relation of fan input when representing such as the blowout of unit outdoor predetermined wind amount, noise and angle [alpha].As shown in figure 23, during α=0 °, fan input and noise are all minimum.This is because during α=0 °, the flowing resistance of the grid of fan protection part is minimum.As can be seen here, angle formed by the grid of fan protection part and fan rotation axis is as far as possible close to 0.
As mentioned above; according to the outdoor unit of pressure fan with embodiment 3; 0 is set to by angle formed by the grid of fan protection part and fan rotation axis; air drag can be made minimum; so; fan input outdoor during unit blowout predetermined wind amount, noise become minimum, can obtain the outdoor unit that running efficiency is high, energy-conservation.
Embodiment 4
Figure 24 is the figure of the propeller type fan 1 representing embodiment 4.In the present embodiment, the shape of propeller type fan 1 is described.The helical fan 1 of present embodiment has the rib 6 from the suction surface outer circumference end of propeller type fan 1 towards direction of principal axis upstream side.
At this, table 1 represents that the pressure fan that propeller type fan 1 has rib 6 and the fan not having the pressure fan of rib 6 when predetermined wind amount input, the value of noise.
[table 1]
Fan input (W) Noise [dB]
There is no rib 6 632 62.1
There is rib 6 630 60.8
As known from Table 1, although fan input is roughly the same, have the pressure fan of rib 6, noise is little.The following describes its reason.First, according to static pressure P st (), defines the rms value of the static pressure variation in straight sections 4 wall of horn mouth 2 with following formula (3) and (4).The rms value of static pressure variation is larger, and the noise produced from wall is larger.
[mathematical expression 1]
p S ( t ) = p &OverBar; S + p S &prime; ( t ) . . . ( 3 )
( : mean value, p s' (t): variation value)
The rms value={ (p of static pressure variation si(t) 2)/N} 0.5(4)
（i=1、2、…、N）
Due to the effect of differential static pressure, the vorticity of that produce near the outer circumference end of propeller type fan 1, from pressure face to suction surface leakage flow and wing tip vortex is larger, and the rms value of static pressure variation is larger, becomes noise source.Rib 6 becomes flowing resistance for the leakage flow from pressure face to suction surface of wing tip vortex, thus stream narrows, so, the generation of wing tip vortex can be suppressed.
Figure 25 represents that the propeller type fan 1 when not having rib 6 rotates the figure of the flow trace line of the wing tip vortex produced.Figure 26 is the figure of the flow trace line of wing tip vortex when indicating rib 6.The rms value of static pressure variation when table 2 indicates apleuria 6.
[table 2]
Rms value [Pa]
There is no rib 6 118.0
There is rib 6 94.4
As shown in figure 26, when having rib 6, little when the vorticity ratio of wing tip vortex does not have a rib 6.Therefore, as shown in table 2, according to the pressure fan of the outdoor unit of embodiment 4, the rms value of the static pressure variation on the wall of horn mouth 2 reduces, and can reduce noise.
Embodiment 5
Figure 27 is the figure of the radius of curvature R of the fillet part 3a in the suction opening portion 3 of the horn mouth 2 representing embodiment 5.In figure 27, the shape in 2 suction opening portions 3 that radius of curvature R is different is represented.
Figure 28 is the figure of the relation representing P-Q characteristic and R/D.Here, this figure is based on following R/D value: establishing fan diameter D, rotating speed N 0for under state that is constant and that fixed by suction opening portion 3 terminal location of horn mouth 2, change the R/D value (hereinafter referred to R/D) during the size of the radius of curvature R of fillet part 3a.In Figure 28, for P-Q characteristic, represent air quantity Q 1, Q 2in R/D.
As shown in figure 28, at air quantity Q 1, no matter R/D how, and static pressure P does not have large difference.In addition, although do not illustrate especially, for air quantity Q 1than sound level K s, fan efficiency η, even if R/D change, also there is no difference.
Figure 29 represents air quantity Q 2than sound level K swith the figure of the relation of R/D.Figure 30 represents air quantity Q 2fan efficiency η and the figure of relation of R/D.As shown in Figure 28 ~ 30, at air quantity Q 2, R/D is larger, and static pressure P, fan efficiency η are higher, than sound level K sless.In addition, P-Q characteristic, K s-Q characteristic, η-Q characteristic diminish in the gradient of open sides.Therefore, at horn mouth 2, the radius of curvature R of fillet part 3a is larger, and static pressure P, the fan efficiency η at the operating point place of open sides more improve, than sound level K sless, so, the reduction of rotating speed, fan input, noise can be realized.
Like this, the radius of curvature R of the fillet part 3a in suction opening portion 3 is larger, and fan efficiency η more improves, than sound level K sless.But due to the reason such as size restriction of such as outdoor unit, in the casing that the length (size) of width and depth (in length and breadth) is different, if complete cycle sets the radius of curvature R of fillet part 3a equably, then overall radius of curvature R reduces.
For this reason, when the aspect rate of outdoor unit casing is different, the fillet part 3a of the part that can expand expands, and makes the terminal location in suction opening portion 3 different, thus makes the aggregate-value of the radius of curvature R of the fillet part 3a of suction opening portion 3 complete cycle maximum.
Embodiment 6
Figure 31 is the pie graph of the refrigerating air-conditioning of embodiment of the present invention 6.In the present embodiment, routine as of the freezing cycle device with above-mentioned pressure fan, refrigerating air-conditioning is described.The refrigerating air-conditioning of Figure 31 has aforesaid outdoor unit (off-premises station) 100 and load cell (indoor set) 200, they is connected and forms main refrigerant loop (hereinafter referred to main refrigerant circuit), make refrigerant circulation by refrigerant piping.Among refrigerant piping, the pipe arrangement that the cold-producing medium (gas refrigerant) of supplied gas flows is called gas pipe arrangement 300, by cold-producing medium (liquid refrigerant for liquid.Also the situation of gas-liquid two-phase cold-producing medium is comprised) pipe arrangement that flows is called liquid pipe arrangement 400.
In the present embodiment, outdoor unit 100 is made up of each device (mechanism) of heat exchanger 108, bypass throttle device 109 and outside control device 110 between compressor 101, oil eliminator 102, cross valve 103, outdoor heat exchanger 104, outside pressure fan 105, reservoir (gas-liquid separator) 106, outside throttling arrangement (expansion valve) 107, cold-producing medium.
Compressor 101 is discharged after the refrigerant compression of suction.Here, compressor 101 has converting means etc., by making operating frequency change arbitrarily, the capacity of compressor 101 (refrigerant amount that time per unit is sent) can be changed imperceptibly.
Oil eliminator 102 mixed lubricating oil separation of discharging from compressor 101 in the refrigerant out.Isolated lubricating oil turns back to compressor 101.Cross valve 103, according to the instruction from outside control device 110, according to when being cooling operation or when heating running, switches the flowing of cold-producing medium.In addition, outdoor heat exchanger 104 carries out the heat exchange of cold-producing medium and air (outdoor air).Such as, when heating running, playing the effect of evaporimeter, making the cold-producing medium of the low pressure flowed into via outside throttling arrangement 107 and air carry out heat exchange, make cold-producing medium evaporate and gasify.In addition, when cooling operation, play the effect of condenser, make from cross valve 103 side inflow, compressor 101, carried out heat exchange by the cold-producing medium that compresses and air, condensation of refrigerant is liquefied.At outdoor heat exchanger 104, in order to effectively carry out the heat exchange of cold-producing medium and air, be provided with the outside pressure fan 105 as the pressure fan illustrated by above-mentioned embodiment 1 ~ 4.To outside pressure fan 105, also at random can change the operating frequency of fan motor with converting means, the rotary speed of propeller type fan 1 is changed imperceptibly.
Heat exchanger 108 between cold-producing medium, flow through refrigerant loop primary flow path cold-producing medium and from this stream branch and by bypass throttle device 109(expansion valve) between the cold-producing medium that have adjusted flow, carry out heat exchange.Especially need in overcooled for cold-producing medium situation when cooling operation, between cold-producing medium, heat exchanger 108 is supplied to indoor set 200 by after cold-producing medium supercooling.Via the liquid that bypass throttle device 109 flows, return reservoir 106 via bypass pipe arrangement.Reservoir 106 is such as the device of the residual refrigerant storing liquid.Outside control device 110 is such as made up of microcomputer etc.Outside control device 110 can with indoor control device 204 wired or wireless communication, according to the detection data of the various testing agencies (sensor) in such as refrigerating air-conditioning, each mechanism of the operating frequency control of the compressor 101 that control utilizes converter circuit controls to carry out etc., refrigerating air-conditioning, thus carry out the action control of whole refrigerating air-conditioning.
On the other hand, load cell 200 is made up of load side heat exchanger 201, load side throttling arrangement (expansion valve) 202, load side pressure fan 203 and load side control device 204.Load side heat exchanger 201 carries out the heat exchange of cold-producing medium and air.Such as, when heating running, playing the effect of condenser, carrying out the heat exchange of cold-producing medium and the air flowed into from gas pipe arrangement 300, after making condensation of refrigerant liquefaction (or gas-liquid two-phase), flowing out to liquid pipe arrangement 400 side.On the other hand, when cooling operation, play the effect of evaporimeter, carry out by load side throttling arrangement 202 and be formed as the cold-producing medium of low-pressure state and the heat exchange of air, make cold-producing medium seize the heat in air and after evaporating gasification, flow out to gas pipe arrangement 300 side.In addition, in load cell 200, be provided with the load side pressure fan 203 of the flowing for regulating the air carrying out heat exchange.The running speed of this load side pressure fan 203 is such as set by user.Load side throttling arrangement 202 changes by making aperture, regulates the pressure of the cold-producing medium in load side heat exchanger 201.
In addition, load side control device 204 is also made up of microcomputer etc., can carry out wired or wireless communication with such as outside control device 110.According to the instruction from outside control device 110, the instruction from occupant etc., each device (mechanism) of control overhead unit 200, makes the temperature that indoor become predetermined.In addition, the signal comprising the detection data of the testing agency being located at load cell 200 is sent.
As mentioned above, in the refrigerating air-conditioning of embodiment 5, in embodiment 1 ~ 4 illustrate pressure fan and outside pressure fan 105 for outdoor unit 100, towards the direction blow out air contrary with gravity direction, like this, can low noise be realized, and increase air quantity, the energy-saving of refrigerating air-conditioning (freezing cycle device) can be realized.
The explanation of Reference numeral
1 ... propeller type fan, 2 ... horn mouth, 3 ... suction opening portion, 3a ... fillet part, 4 ... straight sections, 5 ... blowout opening portion, 5a ... rake, 5b straight sections, 6 ... rib, 10 ... horn mouth metallic plate, 100 ... outdoor unit, 101 ... compressor, 102 ... oil eliminator, 103 ... cross valve, 104 ... outdoor heat exchanger, 105 ... outside pressure fan, 106 ... reservoir, 107 ... outside throttling arrangement, 108 ... heat exchanger between cold-producing medium, 109 ... bypass throttle device, 110 ... outside control device, 200 ... load cell, 201 ... load side heat exchanger, 202 ... load side throttling arrangement, 203 ... load side pressure fan, 204 ... load side control device, 300 ... gas pipe arrangement, 400 ... liquid pipe arrangement

Claims (7)

1. a pressure fan for outdoor unit, has propeller type fan and horn mouth,
Above-mentioned propeller type fan to rotate and to have multiple blades of the flowing of the gas producing the direction contrary with above-mentioned gravity direction centered by the rotating shaft of gravity direction;
Above-mentioned horn mouth, along the direction of rotation of the blade of this propeller type fan, forms the wall of annular, for carrying out rectification to above-mentioned gas in the outside of the outer circumference end of above-mentioned blade;
When the operating point of above-mentioned propeller type fan to be positioned at than surge area more by open sides, the wind path that this horn mouth has a blowout side expand the wall as inclined-plane that formed, and be integrally formed as the shape meeting following relation as condition:
Length H on rotating shaft direction between the suction side on above-mentioned inclined-plane and the terminal of blowout side and the fan diameter D of above-mentioned propeller type fan is the relation of H/D >=0.04;
Connect the relation that the straight line of two terminals on above-mentioned inclined-plane and above-mentioned rotating shaft angulation θ are 0< θ≤60 °; And
The length L of the length L the above-mentioned rotating shaft direction of the suction side terminal part from the opening portion of suction side to above-mentioned inclined-plane and the above-mentioned propeller type fan blade on above-mentioned rotating shaft direction 0, be L/L 0the relation of>=0.5;
Above-mentioned horn mouth, in the opening portion of above-mentioned blowout side, has the wall extended towards above-mentioned rotating shaft direction from the blowout lateral terminal part on above-mentioned inclined-plane.
2. the pressure fan of outdoor unit as claimed in claim 1, is characterized in that,
Also have fan protection part, this fan protection part has the grid of the opening portion covering above-mentioned blowout side;
Grid on above-mentioned rotating shaft direction towards parallel with above-mentioned rotating shaft.
3. the pressure fan of outdoor unit as claimed in claim 1 or 2, is characterized in that, above-mentioned propeller type fan has with above-mentioned rotating shaft overall from each blade outer circumference end or extend to the rib of above-mentioned suction side except the part at the two ends of outer circumference end substantially in parallel.
4. the pressure fan of outdoor unit as claimed in claim 1 or 2, is characterized in that, the scope specified according to the size of the casing of outdoor unit, a part for the opening portion of above-mentioned bell-mouthed above-mentioned blowout side is out of shape.
5. the pressure fan of outdoor unit as claimed in claim 1 or 2, it is characterized in that, above-mentioned horn mouth has the flexure plane of the office, opening portion being formed in suction side, and the value that the radius of curvature in above-mentioned flexure plane adds up along complete cycle is maximum in the condition and range installed or arrange.
6. an outdoor unit, it is characterized in that, having the compressor of compressed refrigerant, carrying out the outdoor heat converter of the heat exchange of cold-producing medium and air and for making above-mentioned air by the pressure fan of this outdoor heat exchanger, above-mentioned pressure fan is the pressure fan that claim 1 or 2 is recorded.
7. a freezing cycle device, is characterized in that, outdoor unit load cell and claim 6 recorded is connected with pipe arrangement and forms refrigerant loop; Above-mentioned load cell has the flow control device of multiple load side heat exchanger heat exchange object and cold-producing medium being carried out heat exchange and the flow regulating the cold-producing medium flowing into this load side heat exchanger.
CN201080069087.8A 2010-09-14 2010-09-14 The pressure fan of outdoor unit, outdoor unit and freezing cycle device Active CN103097821B (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2010/005596 WO2012035577A1 (en) 2010-09-14 2010-09-14 Blower for outdoor unit, outdoor unit, and refrigeration cycle device

Publications (2)

Publication Number Publication Date
CN103097821A CN103097821A (en) 2013-05-08
CN103097821B true CN103097821B (en) 2015-08-19

Family

ID=45831084

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201080069087.8A Active CN103097821B (en) 2010-09-14 2010-09-14 The pressure fan of outdoor unit, outdoor unit and freezing cycle device

Country Status (6)

Country Link
US (1) US20130125579A1 (en)
EP (1) EP2618066B1 (en)
JP (1) JP5611360B2 (en)
CN (1) CN103097821B (en)
HK (1) HK1180758A1 (en)
WO (1) WO2012035577A1 (en)

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2957443B1 (en) * 2013-02-12 2018-05-09 Mitsubishi Electric Corporation Outdoor cooling unit for air conditioning device for vehicle
JP6283194B2 (en) * 2013-10-21 2018-02-21 日立ジョンソンコントロールズ空調株式会社 Air conditioner outdoor unit
JP6385752B2 (en) * 2013-12-02 2018-09-05 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． Outdoor unit for blower and air conditioner
KR20150075934A (en) * 2013-12-26 2015-07-06 엘지전자 주식회사 Brower apparatus and air conditioner having the same
JP6340819B2 (en) * 2014-02-21 2018-06-13 株式会社デンソー Blower
JP2015155681A (en) * 2014-02-21 2015-08-27 株式会社デンソー blower
KR102302546B1 (en) * 2014-12-31 2021-09-15 엘지전자 주식회사 Outdoor unit of air conditioner
JP6379062B2 (en) * 2015-03-17 2018-08-22 日立ジョンソンコントロールズ空調株式会社 Outdoor unit of air conditioner and bell mouth provided therein
US10378781B2 (en) * 2015-06-19 2019-08-13 Mitsubishi Electric Corporation Outdoor unit for refrigeration cycle apparatus, and refrigeration cycle apparatus
JP2017053295A (en) * 2015-09-11 2017-03-16 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． Air blower and outdoor device
JP6422591B2 (en) * 2015-10-23 2018-11-14 三菱電機株式会社 Air conditioner outdoor unit
WO2017077576A1 (en) * 2015-11-02 2017-05-11 三菱電機株式会社 Air conditioner outdoor unit and refrigeration cycle device
WO2017130273A1 (en) * 2016-01-25 2017-08-03 三菱電機株式会社 Outdoor machine and air conditioner provided with same
JP6256516B2 (en) * 2016-04-27 2018-01-10 ダイキン工業株式会社 Refrigeration unit outdoor unit
JP6611676B2 (en) * 2016-06-16 2019-11-27 三菱電機株式会社 Outdoor unit for blower and refrigeration cycle equipment
WO2018016012A1 (en) 2016-07-19 2018-01-25 三菱電機株式会社 Heat source unit and refrigeration cycle device
WO2018131077A1 (en) * 2017-01-10 2018-07-19 三菱電機株式会社 Outdoor unit for air conditioner
WO2020250364A1 (en) * 2019-06-13 2020-12-17 三菱電機株式会社 Axial flow fan, blower device, and refrigeration cycle device
JP7173939B2 (en) * 2019-08-26 2022-11-16 ダイキン工業株式会社 Blower and heat pump unit
WO2021084605A1 (en) * 2019-10-29 2021-05-06 三菱電機株式会社 Outdoor unit for air conditioning device
WO2024047836A1 (en) * 2022-09-01 2024-03-07 Hitachi-Johnson Controls Air Conditioning, Inc. Air-conditioning apparatus and casing structure

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1912506A (en) * 2001-01-31 2007-02-14 三菱电机株式会社 Refrigerating circulation device

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4152094A (en) * 1975-10-31 1979-05-01 Hitachi, Ltd. Axial fan
JP2504521B2 (en) * 1988-04-28 1996-06-05 株式会社東芝 Outdoor unit of air conditioner
KR0140195B1 (en) * 1990-03-07 1998-07-01 다나까 다로오 Press-fit Axial Blowers
US5248224A (en) * 1990-12-14 1993-09-28 Carrier Corporation Orificed shroud for axial flow fan
JP3087876B2 (en) 1993-09-20 2000-09-11 株式会社富士通ゼネラル Outdoor unit of air conditioner
JP3199931B2 (en) 1993-10-08 2001-08-20 株式会社日立製作所 Outdoor unit of air conditioner
JP4190683B2 (en) * 1999-11-22 2008-12-03 株式会社小松製作所 Fan device
JP4140236B2 (en) * 2000-12-28 2008-08-27 ダイキン工業株式会社 Blower and outdoor unit for air conditioner
JP2002250298A (en) * 2001-02-23 2002-09-06 Mitsubishi Heavy Ind Ltd Propeller fan
KR20030035328A (en) * 2001-10-31 2003-05-09 삼성전자주식회사 Outdoor unit of air conditioner
JP2004156884A (en) * 2002-11-08 2004-06-03 Daikin Ind Ltd Fan guard for blower unit
JP3641724B2 (en) * 2003-09-30 2005-04-27 ダイキン工業株式会社 Air conditioner indoor unit
JP4690682B2 (en) * 2004-09-07 2011-06-01 三菱電機株式会社 air conditioner
EP1750014B1 (en) * 2005-08-03 2014-11-12 Mitsubishi Heavy Industries, Ltd. Axial fan for heat exchanger of in-vehicle air conditioner
CN101351676B (en) * 2005-12-30 2011-11-23 开利公司 comfortable system outdoor device with compressor and method of flow characteristics improvement
JP2008014302A (en) * 2006-06-09 2008-01-24 Nippon Densan Corp Axial flow fan
JP2008089271A (en) * 2006-10-04 2008-04-17 Hitachi Appliances Inc Outdoor unit for air conditioner
JP2008232536A (en) * 2007-03-20 2008-10-02 Daikin Ind Ltd Outdoor unit for air conditioner
JP4823294B2 (en) * 2008-11-04 2011-11-24 三菱電機株式会社 Blower and heat pump device using this blower

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1912506A (en) * 2001-01-31 2007-02-14 三菱电机株式会社 Refrigerating circulation device

Also Published As

Publication number Publication date
JPWO2012035577A1 (en) 2014-01-20
EP2618066A4 (en) 2018-04-04
JP5611360B2 (en) 2014-10-22
EP2618066A1 (en) 2013-07-24
HK1180758A1 (en) 2013-10-25
EP2618066B1 (en) 2019-09-04
CN103097821A (en) 2013-05-08
US20130125579A1 (en) 2013-05-23
WO2012035577A1 (en) 2012-03-22

Similar Documents

Publication Publication Date Title
CN103097821B (en) The pressure fan of outdoor unit, outdoor unit and freezing cycle device
CN102639954B (en) Heat exchanger and indoor unit including same
CN101061354B (en) Air-conditioner
JP4800631B2 (en) Structure of blower fan
JP4938241B2 (en) Structure of blower fan
JP4678327B2 (en) Air conditioner
US20190101131A1 (en) Centrifugal Blower, Air Conditioner, and Refrigeration Cycle Apparatus
CN105387592A (en) Air-conditioner
JP2012136941A (en) Blower, outdoor unit and refrigeration cycle device
CN114440316B (en) Air duct assembly and air conditioning equipment with same
JP5709607B2 (en) Fan guard, outdoor unit and refrigeration cycle apparatus
CN110848801A (en) Air duct structure of indoor unit of air conditioner and air conditioner
CN100547303C (en) Indoor set and air-conditioner
CN112128120B (en) Ultra-thin indoor unit
CN110617553A (en) Volute tongue structure of through-flow air duct, air duct system and air conditioner indoor unit
JPH06101909A (en) Cooling device for compressor
CN211261014U (en) Volute tongue structure of through-flow air duct, air duct system and air conditioner indoor unit
CN220669594U (en) Indoor unit of vertical air conditioner
CN211204233U (en) Air duct structure of indoor unit of air conditioner and air conditioner
CN213480380U (en) Indoor air conditioner
CN215909338U (en) Indoor unit and air conditioner with same
CN217582586U (en) Mixed flow fan and ducted air conditioner
CN220750248U (en) Indoor unit of vertical air conditioner
CN211261013U (en) Volute tongue structure of through-flow air duct, air duct system and air conditioner indoor unit
JP5818984B2 (en) Outdoor unit of air conditioner and air conditioner provided with the same

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
REG Reference to a national code

Ref country code: HK

Ref legal event code: DE

Ref document number: 1180758

Country of ref document: HK

C14 Grant of patent or utility model
GR01 Patent grant
REG Reference to a national code

Ref country code: HK

Ref legal event code: GR

Ref document number: 1180758

Country of ref document: HK