CN104603466A - Cross-flow fan - Google Patents
Cross-flow fan Download PDFInfo
- Publication number
- CN104603466A CN104603466A CN201380046041.8A CN201380046041A CN104603466A CN 104603466 A CN104603466 A CN 104603466A CN 201380046041 A CN201380046041 A CN 201380046041A CN 104603466 A CN104603466 A CN 104603466A
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- China
- Prior art keywords
- blade
- cross flow
- flow fan
- auxiliary ring
- blades
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
- F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type
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- 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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
- F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
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- 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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
- F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
- F04D29/283—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis rotors of the squirrel-cage type
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- 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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
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- 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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/663—Sound attenuation
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- 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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/663—Sound attenuation
- F04D29/665—Sound attenuation by means of resonance chambers or interference
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/20—Rotors
- F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
- F05D2240/304—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the trailing edge of a rotor blade
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
A cross-flow fan is configured so that flow path loss caused by an intermediate plate or the like is reduced without reducing the strength of the cross-flow fan. Blades (40) extend in the longitudinal direction from a disk-like or circular ring-like support plate. The ring section (61) of an auxiliary ring (60) is located at the intermediate portion of the blades (40) in the longitudinal direction at a position on the outside of the outer ends (40a) of the blades (40). The connection sections (62) of the auxiliary ring (60) are each extended from the ring section (61) to a position between adjacent blades of the blades (40) and are joined to the blades (40) at the positions between the adjacent blades. Cutouts (40g) are formed in the outer ends (40a) of the blades (40).
Description
Technical field
The present invention relates to cross flow fan.
Background technique
The cross flow fan that the indoor set of air conditioner etc. use, between two the discoid or circular dunnages at two ends being configured at length direction, is configured with the more blades extended along its length.Further, as recorded in patent documentation 1 (Japanese Unexamined Patent Publication 05-87086 publication) etc., between two dunnages, discoid or circular intermediate plate is configured with, to strengthen the intensity of more blades.
Brief summary of the invention
The problem that invention will solve
In addition, when arranging multiple dunnage, produce wind loss due to multiple dunnage, thus when arranging multiple dunnage, stream loss increases.But, if reduce the number of dunnage in order to the stream reducing to be caused by dunnage loses, then cause the intensity of cross flow fan to decline.
Summary of the invention
Problem of the present invention is when not reducing the intensity of cross flow fan, suppresses the stream loss produced in dunnage etc.
For the means of dealing with problems
The cross flow fan of a first aspect of the present invention has: dunnage; More blades, they extend along its length from dunnage, are formed with multiple notch in outer end; And auxiliary ring, it has ring portion and multiple joint, this ring portion is positioned at the intermediate portion of the length direction of more blades, and be configured in the outside of outer end of more blades, described multiple joint extends to from ring portion between the adjacent blades of more blades, and engages with blade between adjacent blades.
According to the cross flow fan of first aspect, auxiliary ring to engage with blade suppress stream loss by only extending to joint between adjacent blades, in the middle part of the length direction of more blades, auxiliary ring engages with blade and by more blades harness, can strengthen the intensity of the fan unit comprising dunnage and more blades thus.But the variable length blade etc. of cross flow fan for this reason, makes the noises such as sound of the wind increase.Therefore, by forming notch in the outer end of blade, can restraint speckle.
The cross flow fan of a second aspect of the present invention is the cross flow fan according to first aspect, and auxiliary ring is configured in the position not forming notch of more blades.
According to the cross flow fan of second aspect, auxiliary ring is configured in the position not forming notch, thus can improve the joint of auxiliary ring and the bond strength of blade, and can suppress the wind speed decreased of the ring portion at auxiliary ring.
The cross flow fan of a third aspect of the present invention is the cross flow fan according to second aspect, and the interval of multiple notch of more blades is configured to, and is greater than the position not configuring auxiliary ring at the position being configured with auxiliary ring.
According to the cross flow fan of the third aspect, the distance from the position to notch being configured with auxiliary ring can be extended, reduce the mutual interference of auxiliary ring and notch, and the wind speed decreased in auxiliary ring portion can be suppressed.
The cross flow fan of a fourth aspect of the present invention is according to the cross flow fan in first ~ third aspect described in any one aspect, auxiliary ring and more blades one-body molded.
According to the cross flow fan of fourth aspect, by by auxiliary ring and more blades one-body molded, do not need the assembling of auxiliary ring and more blades.
The cross flow fan of a fifth aspect of the present invention is according to the cross flow fan in first ~ fourth aspect described in any one aspect, and the thickness of the ring portion of auxiliary ring is along with thinning from inner circumferential side towards outer circumferential side.
According to the cross flow fan of the 5th aspect, the thickness of ring portion, along with thinning towards outer circumferential side, thus can reduce the fluid loss of the air of contact ring portion.
The cross flow fan of a sixth aspect of the present invention is according to the cross flow fan in the first ~ five aspect described in any one aspect, multiple joints of auxiliary ring engage with each suction surface of more blades respectively, and to be formed as from ring portion towards inner side outstanding triangle, engaging with the suction surface of blade of the joint of triangle.
According to the cross flow fan of the 6th aspect, the joint of triangle while engage with the suction surface of blade, thus anastomosis part can be increased, and the pressure side side of blade is not used in connection, thus can reduce the joint of the pressure side side being positioned at blade, the stream loss increased due to joint is suppressed for comparatively low degree.
The cross flow fan of a seventh aspect of the present invention is according to the cross flow fan in the first ~ six aspect described in any one aspect, and the shape of the notch of more blades is the triangle broadened towards the direction of outer end.
According to the cross flow fan of the 7th aspect, by notch is set to triangle, the vortex downsizing that produces due to the blowout air-flow from fan can be made and sectionalization, thus reduce noise.
The cross flow fan of a eighth aspect of the present invention is according to the cross flow fan in the first ~ seven aspect described in any one aspect, and more blades is at least different from each other in the shape of the chien shih notch of adjacent one group of blade.
According to the cross flow fan of eighth aspect, different by the shape of the chien shih notch at adjacent blade, the regularity of the flowing of the wind produced at notch can be upset, reduce the vibration of the air produced at notch.
The cross flow fan of a ninth aspect of the present invention is according to the cross flow fan in first ~ eighth aspect described in any one aspect, and more blades makes the configuration space of mutually adjacent blade at least different at a place.
According to the cross flow fan of the 9th aspect, by making the configuration space of adjacent blade different, the regularity of the movement of blade can be upset, the vibration of the air produced due to the movement of blade can be suppressed.
The cross flow fan of a tenth aspect of the present invention is according to the cross flow fan in the first ~ nine aspect described in any one aspect, dunnage comprises multiple dunnage, auxiliary ring comprises multiple auxiliary ring, be formed with multiple fan unit, described fan unit is by one-body molded to a dunnage, an auxiliary ring and more blades and obtain, and at least one group of mutually adjacent fan unit to stagger the angle of regulation and mutually fastening in the blade of the mutually adjacent fan unit mode do not arranged point-blank.
According to the cross flow fan of the tenth aspect, do not arrange point-blank between adjacent fan unit by making blade, the regularity of the movement of the blade between adjacent fan unit can be upset, the vibration of the air produced along with the movement of the blade of adjacent fan unit can be suppressed.
Invention effect
In the cross flow fan of a first aspect of the present invention, stream loss can not only be reduced when not reducing the intensity of cross flow fan, and the suppression to noise can be realized.
In the cross flow fan of a second aspect of the present invention, auxiliary ring is configured in the position not forming notch, can realize the raising of the intensity of cross flow fan and the reduction of stream loss thus.
In the cross flow fan of a third aspect of the present invention, can extend the distance between auxiliary ring and notch, the inhibition of the wind speed decreased of the ring portion of auxiliary ring improves.
In the cross flow fan of a fourth aspect of the present invention, the assembling of auxiliary ring and more blades can be saved, thus can cutting down cost.
In the cross flow fan of a fifth aspect of the present invention, by making the thickness of ring portion along with thinning towards outer circumferential side, the fluid loss of air can be reduced, improving Diffusion performance.
In the cross flow fan of a sixth aspect of the present invention, the structure engaged with the suction surface of blade of the joint of triangle can be utilized, realize the reduction of stream loss and the raising of the effect that prevents intensity from declining of cross flow fan simultaneously.
In the cross flow fan of a seventh aspect of the present invention, the reduction effect of sound of the wind improves.
In the cross flow fan of a eighth aspect of the present invention, different by the shape of the chien shih notch at adjacent blade, can sound of the wind be reduced.
In the cross flow fan of a ninth aspect of the present invention, by making the configuration space of adjacent blade different, sound of the wind can be reduced.
In the cross flow fan of a tenth aspect of the present invention, by making blade not arrange point-blank between adjacent fan unit, sound of the wind can be reduced.
Accompanying drawing explanation
Fig. 1 is the sectional view of the summary of the indoor set that aircondition is shown.
Fig. 2 is the stereogram of the summary of the impeller of the cross flow fan that a mode of execution is shown.
Fig. 3 is the stereogram of an operation of the assembling of impeller for illustration of cross flow fan.
Fig. 4 is the planimetric map of an example of the structure of the end plate that impeller is shown.
Fig. 5 is the stereogram of an example of the structure of the end plate that impeller is shown.
Fig. 6 is the side view of an example of the structure of the end plate that impeller is shown.
Fig. 7 is the planimetric map of an example of the structure of the dunnage that fan unit is shown.
Fig. 8 is the sectional view of an example of the structure of the auxiliary ring that fan unit is shown.
Fig. 9 is the close-up plan view of the structure for illustration of the fan unit shown in Fig. 5.
Figure 10 is the Partial enlarged side view of the structure for illustration of the fan unit shown in Fig. 6.
Figure 11 is the side view of another example of the structure of the fan unit that impeller is shown.
Figure 12 is the side view of another example of the structure of the fan unit that impeller is shown.
Figure 13 is the side view of another example of the structure that impeller is shown.
Figure 14 is the stereogram that the structure of carrying out other fan unit contrasted with the fan unit of Fig. 5 is shown.
Embodiment
Below, about the cross flow fan of one embodiment of the present invention, be described for the cross flow fan arranged in the indoor set of aircondition.
(1) cross flow fan in indoor set
Fig. 1 is the figure of the overview in the cross section of the indoor set 1 that aircondition is shown.Indoor set 1 has main body cover 2, air filter 3, indoor heat converter 4, cross flow fan 10, vertical baffle 5 and horizontal baffle 6.As shown in Figure 1, in the downstream side of the suction port 2a of the end face of main body cover 2, be configured with air filter 3 opposedly with suction port 2a.Indoor heat converter 4 is configured with in the further downstream side of air filter 3.All passed through at air filter 3 by the indoor air of suction port 2a arrival indoor heat converter 4 and be removed dust.
Front face side heat exchanger 4a and back side heat exchanger 4b are connected in the shape of falling V to observe from the side and are formed by indoor heat converter 4.When the top view observed from the end face of main body cover 2, front face side heat exchanger 4a is configured in the position opposed with the roughly front face side half of suction port 2a, and back side heat exchanger 4b is configured in the position opposed with the roughly back side half of suction port 2a.Front face side heat exchanger 4a and back side heat exchanger 4b all by by multiple plate fin along the width direction of indoor set 1 arranged in parallel be installed on heat conductive tube and form.Suck from suction port 2a and pass through the indoor air of air filter 3, through front face side heat exchanger 4a and back side heat exchanger 4b time produce heat exchange, carry out air adjustment and.
In the downstream side of indoor heat converter 4, the cross flow fan 10 of substantially cylindrical shape extends in long way along the width direction of main body cover 2, arranges abreast together with indoor heat converter 4 with the width direction of main body cover 2.Cross flow fan 10 has: impeller 20, and it is configured in and is clipped by the indoor heat converter 4 of the shape of falling V and in the space be surrounded by it; With fan motor (not shown), it is for drives impeller 20.This cross flow fan 10 make arrow from impeller 20 to Fig. 1 shown in direction A1 (clockwise) rotate and produce air-flow.
The blowout passage be connected with the blow-off outlet 2b in the downstream of cross flow fan 10 forms back side by scroll element 2c.Scroll element 2c observes from front has the width roughly the same with the opening portion of the blow-off outlet 2b of main body cover 2.The upper end of scroll element 2c is positioned at the position more top than the upper end of cross flow fan 10, observes the position of the central shaft deflection back side be positioned at than the cross flow fan 10 of cylindrical shape from the side.The lower end of scroll element 2c is connected with the opening end of blow-off outlet 2b.The guide surface of scroll element 2c from cross-section in the level and smooth curve shape in cross flow fan 10 side with centre of curvature so that by the air blown out from cross flow fan 10 smoothly and be directed to blow-off outlet 2b imperturbably.
(2) general structure of the impeller of cross flow fan
Fig. 2 shows the general structure of the impeller 20 of cross flow fan 10.End plate 21,24 and 3 fan units 30 such as engage and form by impeller 20.End plate 21 is configured in one end of impeller 20, and axle center O has metal running shaft 22.Further, in the end plate 24 with blade 40 and auxiliary ring 60 of the other end being configured at impeller 20, the hub portion (not shown) be connected with fan motor axis (not shown) is located at the central part of this end plate 24 usually.Or, also there is the situation that the end plate 24 being configured at the other end of impeller 20 has other structure, there are as being configured to the parts be combined with a part for fan motor, and at central part, there is metal shaft etc.The hub portion (or metal shaft) of the end plate 24 of the running shaft 22 of end plate 21 and the other end of impeller 20 is support, and impeller 20 rotates around axle center O.This end plate 21 adopts and end plate identical in the past.But the structure of end plate 21 does not need identical with the past, suitably can change the structure of end plate 21, to be suitable for the present invention.
Each fan unit 30 has more blades 40, circular dunnage 50 and auxiliary ring 60 respectively.When assembling impeller 20, the more blades 40 of each fan unit 30 self is fused in the dunnage 50 or end plate 21 of adjacent fan unit 30.Fig. 3 shows the operation that two mutually adjacent fan units 30 are fused.Usually, end plate 21 is first placed on fixture 103, is embedded in its recess 23 by the terminal part 40d of the blade 40 of fan unit 30, and the dunnage 50 making soldering tip (horn) 102 contact fan unit 30 carries out ultrasonic fusing.Then, as shown in Figure 3, the terminal part 40d of the blade 40 of follow-up fan unit 30 was embedded previously in the recess 51 of the dunnage 50 of the fan unit 30 of welding, carried out ultrasonic fusing with the dunnage 50 previously equally making soldering tip 102 contact follow-up fan unit 30.Now, clamping from peripheral direction the dunnage 50 be fused makes it not eccentric.Repeatedly carry out this operation, finally make soldering tip 102 contact the end plate 24 with blade 40 and carry out welding.When such welding, be formed with at end plate 21 recess 23 that quantity is identical with blade 40 as shown in Figure 4, blade 40 is positioned end plate 21.Each recess 23 has the plane shape slightly larger than the sectional shape of each blade 40, and thus each blade 40 to embed respectively in each recess 23 and is embedded in this.A recess 23 only in multiple recess 23 is formed with end difference 23a, to carry out the location of end plate 21 and fan unit 30.
(3) concrete structure of fan unit
The concrete structure of the fan unit 30 of present embodiment is as shown in Fig. 5 ~ Figure 10.Fig. 5 is the stereogram of the fan unit 30 illustrated in multiple fan units 30 of the impeller 20 shown in pie graph 2, and Fig. 6 is the side view of this fan unit 30.Fan unit 30 shown in Fig. 5 and Fig. 6 is by being that main material is consisted of integrated more blades 40, dunnage 50 and auxiliary rings 60 such as molding and forming with thermoplastic resin.The sense of rotation of fan unit 30 is direction A1 shown in arrow of Fig. 5.
(3-1) blade
More blades 40 is from first surface 50a (direction along axle center O) extension along its length of circular dunnage 50.Blade 40 is by one-body molded with dunnage 50, thus blade base 40c is fixed on the first surface 50a of dunnage 50, and the opposition side of the blade base 40c of the length direction of blade 40 becomes blade end portion 40d.The length L1 (from blade base 40c to the size of blade end portion 40d) of blade 40 is such as about 10cm.Blade 40 has suction surface 40f and pressure side 40e.Arrow from fan unit 30 to Fig. 5 shown in direction A1 rotate time, the pressure of the pressure side 40e side of blade 40 raises, and the pressure of suction surface 40f side reduces.
The blade end portion 40d of a slice blade 40 only in more blades 40 is formed with notch 40i.This notch 40i is the part of location for carrying out two fan units 30 or carries out the part of location of fan unit 30 and end plate 21, is the part chimeric with the end difference 51c of the end difference 23a of the recess 23 of above-mentioned end plate 21 or the recess 51 of fan unit described later 30.By arranging notch 40i, each recess 51 of each recess 23 of each blade 40 and end plate 21 or fan unit 30 can be made so corresponding one to one.Namely, notch 40i is arranged based on following object: when blade 40 is when the configuration of circumference is uneven or when the shape of blade 40 (thickness and inclination etc.) is uneven, make the terminal part 40d of blade 40 and recess 51 one to one correspondence prevent mistake chimeric.
(3-2) dunnage
Fig. 7 represents the state of observing circular dunnage 50 from bottom surface, namely carries out the state of observing from second surface 50b side.The recess 51 embedded for blade 40 is formed at the second surface 50b opposed with first surface 50a of dunnage 50.Each recess 51 has the plane shape slightly larger than the sectional shape of each blade 40, and thus when two fan units 30 are overlapping, each blade 40 to embed respectively in each recess 51 and is embedded in this.Inner circumferential along dunnage 50 is formed with the protuberance 52 of the ring-type higher than second surface 50b.The outer circumferential side of protuberance 52 tilts sideling, plays the effect when two fan units 30 are overlapping, blade 40 being guided to recess 51.
The periphery 51a of the recess 51 of the outer end 40a contact of blade 40 is positioned at the inner side of the periphery 50c of dunnage 50, and the inner circumferential 51b of the recess 51 of the inner 40b contact of blade 40 is positioned at the outside of the inner circumferential 50d of dunnage 50.In other words, the distance d1 (distance to the outer end 40a of blade 40) from the center (point the O of axle center) of dunnage 50 to the periphery 51a of recess 51 is less than the radius r 1 from the center of dunnage 50 to periphery 50c.Further, the distance d2 (distance to the inner 40b of blade 40) from the center (point the O of axle center) of dunnage 50 to the inner 51b of recess 51 is larger than the radius r 2 from the center of dunnage 50 to inner circumferential 50d.This dunnage 50 is set to and makes the width W 1 (radius r 1-radius r 2) of dunnage 50 be greater than distance (distance d1-distance d2) from the outer end 40a of blade 40 to the radial direction of inner 40b, to make the intensity that the intensity of support blade 40 keeps higher.
(3-3) auxiliary ring
Auxiliary ring 60 is positioned at the intermediate portion of the length direction of blade 40, and from auxiliary ring 60 to the distance of blade base 40c is, 60% of the size (the length L1 of blade 40) from blade base 40c to blade end portion 40d.The allocation position of auxiliary ring 60 preferably leaves the distance of more than 55% of length L1 from blade base 40c, to improve the intensity of cross flow fan 10, make easily to carry out the assembly processes such as ultrasonic fusing.But the allocation position of auxiliary ring 60 not necessarily needs to leave more than 55% of length L1 from blade base 40c, as long as be positioned at the intermediate portion of the length direction of blade 40.According to above-mentioned explanation, the concept of the intermediate portion of the length direction of blade 40 also comprises and is positioned at a little mode departing from Centromedian position.
Fig. 8 shows the sectional shape of the anastomosis part of auxiliary ring 60 and blade 40.Cross section shown in Fig. 8 is the cross section presented when the face vertical with axle center O cuts off.In fig .9, the auxiliary ring 60 when observing from the blade end portion 40d of blade 40 towards blade base 40c and blade 40 and dunnage 50 partial enlargement are illustrated.Auxiliary ring 60 is primarily of ring portion 61, joint 62 and be connected assisting section 63 and form.The radius r 3 of the periphery 61a of ring portion 61 is greater than the radius r 1 of the periphery 51a of dunnage 50.Further, the radius r 3 of the periphery 61a of ring portion 61 is greater than the distance d1 from the center (point the O of axle center) of auxiliary ring 60 to the outer end 40a of blade 40.That is, the periphery 61a of ring portion 61 passes through in the outside of the outer end 40a of all blades 40.In this auxiliary ring 60, the radius r 4 of the inner circumferential 61b of ring portion 61 is greater than the radius r 2 of the inner circumferential 50d of dunnage 50, and less times greater than the distance d1 of outer end 40a to blade 40, the inner circumferential 61b of ring portion 61 passes through near the outside of the outer end 40a of blade 40.
Joint 62 is observed from the direction of axle center O and is formed as the triangle outstanding from ring portion 61 towards inner side.The joint 62 of shape triangular in shape has 3 tops 62a, 62b, 62c, and the limit between top 62a, 62b is connected with ring portion 61, and the limit between top 62a, 62c is connected with the suction surface 40f of blade 40.On the other hand, the pressure side 40e of blade 40 is not connected with joint 62.The length L4 (length between 62a to the 62c of top) of the part that joint 62 is connected with suction surface 40f is shorter than 1/2nd of chord of foil length L3.By being set to that to make the length L4 of the part be connected with suction surface 40f shorter than 1/2nd of chord of foil length L3, and be set to that compared with the situations longer than 1/2nd of chord of foil length L3, Diffusion performance improves.
Be formed near the outer end 40a of blade 40 and connect assisting section 63.Connecting assisting section 63 is the outer end 40a of landfill blade 40 and the part between joint 62 and ring portion 61, for the connection of this three auxiliary.
Enlargedly show a part for the auxiliary ring 60 observed from the side in Fig. 10.Auxiliary ring 60 has the first surface 60a of 40d side, blade end portion, second surface 60b, the outer circumferential face 60c of blade base 40c side and inner peripheral surface 60d.Be formed with the curved surface 60e of radius of curvature R 1 in the part connecting this first surface 60a and outer circumferential face 60c, be formed with the curved surface 60f of radius of curvature R 2 in the part connecting this second surface 60b and outer circumferential face 60c.
The thickness of auxiliary ring 60 is along with thinning from inner circumferential side towards outer circumferential side.That is, auxiliary ring 60 is less than thickness t1 near blade base 40c at the thickness t2 of outer circumferential face 60c.More carefully observe, be set to by auxiliary ring 60, the tiltangleθ 1 making first surface 60a crossing with the face vertical relative to axle center O is greater than the tiltangleθ 2 that the second surface 60b face vertical with this is intersected.In addition, the thickness t1 of auxiliary ring 60 is set to the thickness t3 being less than dunnage 50.
(3-4) notch
As shown in Figure 5 and Figure 6, multiple notch 40g is formed with at blade 40.Recess 40h is formed around each notch 40g.Each notch 40g is formed at the outer end 40a of each blade 40.Notch 40g observes shape triangular in shape from the direction vertical with the suction surface 40f of each blade 40, and broadens towards outer end 40a.Thus, in fan blowout region, the downsizing of rear stream whirlpool and sectionalization can be made, thus restraint speckle.In this fan unit 30, the distance d3 between mutually adjacent notch 40g is set between the notch 40g which is adjacent all identical.
The thickness of recess 40h is the thinnest in the part of the V-shaped contacted with notch 40g.Such as, the thickness of the thickness of the part of V-shaped and the outer end 40a of blade 40 is roughly equal.Each recess 40h is that C font surrounds notch 40g, tilts smoothly from suction surface 40f towards notch 40g.In this recess 40h, do not have concavo-convex from suction surface 40f towards notch 40g, be thus difficult to produce noise.Further, there is no ladder from suction surface 40f towards notch 40g, be thus difficult to produce noise.
Auxiliary ring 60 is configured in the position not forming notch 40g between two notch 40g of the central part of each blade 40.
(4) variation
(4-1) in the above-described embodiment, describe the situation that an auxiliary ring 60 is set at a fan unit 30, but also multiple auxiliary ring 60 can be set at a fan unit 30.
(4-2) in the above-described embodiment, the radius r 3 describing the periphery 61a of ring portion 61 is greater than the situation of the radius r 1 of the periphery 51a of circular dunnage 50, but also the radius r 3 of the periphery 61a of ring portion 61 can be set to identical with the radius r 1 of the periphery 51a of dunnage 50.
(4-3) in the above-described embodiment, the radius r 4 describing the inner circumferential 61b of ring portion 61 compares the slightly large situation of the distance d1 of the outer end 40a of blade 40, but it is equal with distance d1 also can be configured to radius r 4, the inner circumferential 61b of ring portion 61 passes through at the outer end 40a of blade 40.
(4-4) in the above-described embodiment, the shape describing auxiliary ring 60 is circular situation, but the shape of auxiliary ring 60 is not limited to circular, also can be such as have the polygonal shape with the angle of the sheet number equal number of blade 40, can also be the shape in outer circumference end with sawtooth (multiple rag).
(4-5) in the above-described embodiment, describe the situation that the shape of all notch 40g of fan unit 30 is as shown in Figure 6 identical, but the shape of notch also can be made different.Such as, also can the shape of notch 40g, 40j each other be made like that different by mutually adjacent blade 401,402 as shown in figure 11.In addition, also can being configured to variform one group of blade 401,402 of notch be configured continuously (as the structure that blade 401 and blade 402 alternately occur when enclosing around fan unit 30 1), each fan unit 30 can also be configured at as shown in figure 11.
Different by the shape of chien shih notch 40g, the 40j at adjacent blade 401,402, the regularity of the flowing of the wind produced at notch 40g, 40j can be upset.Consequently, the vibration of the air produced at notch 40g, 40j can be reduced, can sound of the wind be reduced.
In addition, the shape of the notch that this place is said is different, conceptually not only comprises notch 40g shape triangular in shape and notch 40j is the difform situation of circular arc as shown in figure 11, and comprises same shape but the different situation of size.
In addition, herein illustrating the variform situation of notch 40g, 40j, but also can be configured to, when making the shape of notch 40g, 40j different, also make the shape of recess 40h different accordingly, or only make the shape of recess different between mutually adjacent blade 40.
(4-6) in the above-described embodiment, describe the situation that the disposition interval (the distance d3 between mutually adjacent notch 40g) of all notch 40g of fan unit 30 is as shown in Figure 6 identical, but the disposition interval of notch also can be made different.Such as, also can be set to as shown in figure 11, make the distance d4 at the position being configured with auxiliary ring 60 be greater than the distance d3 at the position not configuring auxiliary ring 60.
According to when setting shown in Figure 11, can make from the distance (being roughly 1/2nd distances of distance d4) at the position to notch 40g being configured with auxiliary ring 60 longer than the situation (being roughly 1/2nd of distance d3) shown in Fig. 6.Consequently, auxiliary ring 60 and the mutual interference of notch 40g can be reduced, improve in the inhibition of the wind speed decreased of the ring portion 61 of auxiliary ring 60.
(4-7) in the above-described embodiment, describe the situation that the configuration space of blade 40 is identical, also can as shown in figure 12, make configuration space L5, L6 of mutually adjacent blade 403,404,405,406 different.At this, only make the blade 405 in a fan unit 30 different with this place of blade 406.But, make the different position of the configuration space of blade also can be have many places in each fan unit, such as, also can will be set as the configuration space L7 different from configuration space L4, L5 between blade 403 and blade 404.At this, the configuration space of blade refers to when along the cross-section vertical with central shaft O, the distance from the position of centre of gravity of a slice blade 403 to the position of centre of gravity of adjacent blade 404.
The following state repeatedly when the configuration space of blade 40 is identical: according to fan unit 30 being revolved the time (tf/nf) of turning around time tf required and obtaining divided by the quantity nf of the blade 40 of fan unit 30, blade 40 is present in identical position.When carrying out like this blade 40 mobile regularly, the easily noise of the frequency that generation is corresponding with the value of tf/nf.When making configuration space L5, L6 of blade 403,404,405,406 different as shown in figure 12, there is the blade 406 that blade 40 does not arrive origin-location after the time (tf/nf), the regularity of the movement of blade 40 is upset.Therefore, it is possible to suppress the vibration of the air produced due to the movement of blade 40, sound of the wind can be reduced.
(4-8) in the above-described embodiment, be configured to as shown in Figure 2 the blade 40 of mutually adjacent fan unit 30 is arranged point-blank.But, also can not by the blades arrangement of mutually adjacent fan unit point-blank.Such as, as shown in figure 13, not arrange mode point-blank as the blade 407,408 of mutually adjacent fan unit 310,320, in the position of the angle θ 3 of the regulation that staggers separately, ultrasonic fusing is carried out to fan unit 310,320.By not arranged point-blank by blade 407,408 between adjacent fan unit 310,320 like this, the regularity of blade 407,408 movement between adjacent fan unit 310,320 can be upset.Consequently, the vibration of the air produced along with the movement of the blade 407,408 of adjacent fan unit 310,320 can be suppressed, can sound of the wind be reduced.
(5) feature
(5-1) as described above, the ring portion 61 of auxiliary ring 60 is positioned at the intermediate portion of the length direction of more blades 40,401 ~ 408, and is configured in the outside of outer end 40a of more blades 40,401 ~ 408.Further, multiple joints 62 of auxiliary ring 60 extend to from ring portion 61 between the adjacent blades of more blades 40,401 ~ 408 respectively, and engage with blade 40,401 ~ 408 between adjacent blades, are formed with multiple notch 40g, 40j at this outer end 40a.Between adjacent blades, in other words refer to the region clipped by the suction surface 40f of the pressure side 40e of a slice blade 40,401 ~ 408 in more blades 40,401 ~ 408 and adjacent blade 40,401 ~ 408.
Auxiliary ring 60 to engage with blade 40,401 ~ 408 suppress stream loss by only extending to joint 62 between adjacent blades.Simultaneously, at the intermediate portion of the length direction of more blades 40,401 ~ 408, circular ring portion 61 is by more blades 40 harness, and the intensity comprising the fan unit 30,310,320 of circular dunnage 50 and more blades 40,401 ~ 408 is thus strengthened.
Auxiliary ring 60 to engage with blade 40,401 ~ 408 suppress stream loss by only extending to joint 62 between adjacent blades.Simultaneously, at the intermediate portion of the length direction of more blades 40,401 ~ 408, circular ring portion 61 is by more blades 40,401 ~ 408 harness, and the intensity comprising the fan unit 30,310,320 of circular dunnage 50 and more blades 40,401 ~ 408 is thus strengthened.It causes on the other hand the blade 40 of fan unit 30,310,320,401 ~ 408 elongated etc., and the noises such as sound of the wind increase, but can carry out restraint speckle and increase by forming notch 40g, 40j at the outer end 40a of blade 40,401 ~ 408.
Such as, in order to obtain the unit similar to the fan unit 30 of length L1, also can consider to replace auxiliary ring 60 and the following structure that is formed as shown in figure 14: with two fan units 130 that circular dunnage 150 engagement blade 140 is shorter.At this, the structure of dunnage 150 is structures identical with above-mentioned dunnage 50.By two fan units 130 shown in such Figure 14 compared with the fan unit of shown in Fig. 5 30, although intensity when forming impeller is roughly the same, but in structure as shown in figure 14, dunnage 150 is positioned at the centre of fan unit, thus, compared with the situation of auxiliary ring 60, the stream loss of two fan units 130 increases.In addition, in structure as shown in figure 14, add the operation for engaging two fan units 130, the cost thus assembling cost also rises.
In addition, describing dunnage 50 is in the above-described embodiment circular situations, but when dunnage is discoid, also can be made like with time circular, when using discoid dunnage, also play the effect same with during the dunnage 50 that use is circular.
(5-2) specifically, auxiliary ring 60 is configured in the position not forming notch 40g, 40j of more blades 40,401 ~ 408.According to such structure, the joint 62 of auxiliary ring 60 and the bond strength of blade 40,401 ~ 408 can be improved, the wind speed decreased of the ring portion 61 at auxiliary ring 60 can be suppressed.
(5-3) in above-mentioned cross flow fan 10, auxiliary ring 60 and more blades 40,401 ~ 408 resin is formed, and auxiliary ring 60 is by molding and forming etc. and more blades 40,401 ~ 408 one-body molded.By by one-body molded to auxiliary ring 60 and more blades, do not need the assembling of auxiliary ring and more blades, can cutting down cost.Equally, dunnage 50 is also formed with resin, with more blades 40,401 ~ 408 and auxiliary ring 60 simultaneously by molding and forming etc. with auxiliary ring 60 and more blades 40,401 ~ 408 one-body molded.Therefore, the cost cutting effect realized by reducing assembly work increases further.
(5-4) in addition, the thickness of the ring portion 61 of auxiliary ring 60 is along with thinning from inner circumferential side towards outer circumferential side.That is, the thickness t1 of inner circumferential side is greater than the thickness t2 of outer circumferential side.Therefore, it is possible to reduce air at the fluid loss of auxiliary ring 60, Diffusion performance can be improved.Further, the thickness of preferred auxiliary ring 60 is from joint 62 until ring portion 61 is all along with thinning towards outer circumferential side.In this case, Diffusion performance can be improved further.In addition, the Thickness Ratio inner circumferential side of the outer circumferential side of auxiliary ring 60 is thin, from mould, thus easily take out the fan unit 30 of cross flow fan 10 when molding and forming.
(5-5) in addition, each joint 62 is formed as the triangle outstanding from ring portion 61 towards inner side.Further, (limit between top 62a and top 62c) of the joint 62 of triangle engages with the suction surface 40f of blade 40,401 ~ 408.Due to the joint 62 by triangle while engage with the suction surface 40f of blade 40,401 ~ 408, thus can according to joint 62 area increase anastomosis part.On the other hand, one in the summit pressure side side being positioned at other blade, thus can suppress the stream loss increased due to joint for lower degree.According to this structure, the reduction of stream loss and the raising of the effect that prevents intensity from declining of cross flow fan 10 can be realized simultaneously.The limit between each top 62a, 62b, 62c of above-mentioned joint 60 is roughly linearly, but each limit also can be concavo-convex a little.
(5-6) shape of the notch 40g of more blades 40,401 ~ 408 is the triangle expanded towards the direction of outer end.By notch 40g is set to triangle, and such as shape be set to compared with U-shaped, air can smooth flow, suppresses air in the vibration of notch 40g.Consequently, the reduction effect of sound of the wind improves.
Label declaration
10 cross flow fans; 20 impellers; 30,310,320 fan units; 40,401 ~ 408 blades; 50 dunnages; 60 auxiliary rings.
[prior art document]
[patent documentation]
Patent documentation 1: Japanese Unexamined Patent Publication 05-87086 publication
Claims (10)
1. a cross flow fan, this cross flow fan has:
Dunnage (50);
More blades (40,401 ~ 408), they extend along its length from described dunnage, are formed with multiple notch (40g, 40j) in outer end; And
Auxiliary ring (60), it has ring portion (61) and multiple joint (62), this ring portion is positioned at the intermediate portion of the length direction of blade described in multi-disc, and be configured in the outside of described outer end of blade described in multi-disc, described multiple joint extends to from described ring portion between the adjacent blades of blade described in multi-disc, and engages with described blade between described adjacent blades.
2. cross flow fan according to claim 1, wherein,
Described auxiliary ring is configured in the position not forming described notch of blade described in multi-disc.
3. cross flow fan according to claim 2, wherein,
The interval of the multiple described notch of blade described in multi-disc is configured to, and is greater than the position not configuring described auxiliary ring at the position being configured with described auxiliary ring.
4. according to the cross flow fan in claims 1 to 3 described in any one, wherein,
Described in described auxiliary ring and multi-disc, blade is one-body molded.
5. according to the cross flow fan in Claims 1 to 4 described in any one, wherein,
The thickness of the described ring portion of described auxiliary ring is along with thinning from inner circumferential side towards outer circumferential side.
6. according to the cross flow fan in Claims 1 to 5 described in any one, wherein,
The multiple described joint of described auxiliary ring engages with each suction surface (40f) of blade described in multi-disc respectively, and to be formed as from described ring portion towards inner side outstanding triangle, engaging with the described suction surface of described blade of the described joint of described triangle.
7. according to the cross flow fan in claim 1 ~ 6 described in any one, wherein,
The shape of the described notch of blade described in multi-disc is the triangle broadened towards the direction of described outer end.
8. according to the cross flow fan in claim 1 ~ 7 described in any one, wherein,
Blade described in multi-disc at least described in adjacent one group blade chien shih described in the shape of notch different from each other.
9. according to the cross flow fan in claim 1 ~ 8 described in any one, wherein,
Blade described in multi-disc makes the configuration space of mutually adjacent described blade at least different at a place.
10. according to the cross flow fan in claim 1 ~ 9 described in any one, wherein,
Described dunnage comprises multiple dunnage,
Described auxiliary ring comprises multiple auxiliary ring,
Be formed with multiple fan unit, this fan unit by one-body molded for blade described in a described dunnage, a described auxiliary ring and multi-disc and obtain,
Fan unit described in mutually adjacent at least one group (310,320) with the described blade of mutually adjacent described fan unit (407, the 408) mode do not arranged point-blank stagger regulation angle (θ 3) and mutually fastening.
Applications Claiming Priority (7)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012194255A JP5590081B2 (en) | 2012-09-04 | 2012-09-04 | Cross flow fan |
| JP2012-194255 | 2012-09-04 | ||
| JP2012-194256 | 2012-09-04 | ||
| JP2012194256A JP5704139B2 (en) | 2012-09-04 | 2012-09-04 | Cross flow fan |
| JP2012-216122 | 2012-09-28 | ||
| JP2012216122A JP5590088B2 (en) | 2012-09-28 | 2012-09-28 | Cross flow fan |
| PCT/JP2013/073145 WO2014038467A1 (en) | 2012-09-04 | 2013-08-29 | Cross-flow fan |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104603466A true CN104603466A (en) | 2015-05-06 |
Family
ID=50237079
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380046041.8A Pending CN104603466A (en) | 2012-09-04 | 2013-08-29 | Cross-flow fan |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP2894345A4 (en) |
| CN (1) | CN104603466A (en) |
| WO (1) | WO2014038467A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109538514A (en) * | 2019-01-21 | 2019-03-29 | 湖北工程职业学院 | A kind of crossflow fan of damping noise reduction |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR102203939B1 (en) * | 2014-01-06 | 2021-01-18 | 삼성전자주식회사 | Guide blade and air conditioner having the same |
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| JPH0587086A (en) * | 1991-09-05 | 1993-04-06 | Sanko Gosei Kk | Cylindrical impeller |
| CN1118843A (en) * | 1994-08-09 | 1996-03-20 | 东芝株式会社 | Transversly blowing fan |
| JP2001263285A (en) * | 2000-03-21 | 2001-09-26 | Mitsubishi Electric Corp | Thorough flow air blower and air conditioner |
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| CN102341601A (en) * | 2009-03-10 | 2012-02-01 | 大金工业株式会社 | Crossflow fan and air conditioner provided with same |
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|---|---|---|---|---|
| GB986222A (en) * | 1960-02-15 | 1965-03-17 | Firth Cleveland Ltd | Improvements relating to bladed rotors for flow machines and apparatus for making such rotors |
| JPS56136192U (en) * | 1980-03-14 | 1981-10-15 | ||
| JPH03229991A (en) * | 1990-02-05 | 1991-10-11 | Matsushita Electric Ind Co Ltd | Cross-flow air blower |
| 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 |
| JP4973249B2 (en) * | 2006-03-31 | 2012-07-11 | ダイキン工業株式会社 | Multi-wing fan |
| JP4918650B2 (en) * | 2006-06-23 | 2012-04-18 | ダイキン工業株式会社 | Multi-wing fan |
| JP4433093B2 (en) * | 2008-05-09 | 2010-03-17 | ダイキン工業株式会社 | Cross flow fan and air conditioner equipped with the same |
| JP4775867B1 (en) * | 2010-03-15 | 2011-09-21 | シャープ株式会社 | Fan, molding die and fluid feeder |
-
2013
- 2013-08-29 WO PCT/JP2013/073145 patent/WO2014038467A1/en active Application Filing
- 2013-08-29 EP EP13836035.9A patent/EP2894345A4/en not_active Withdrawn
- 2013-08-29 CN CN201380046041.8A patent/CN104603466A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0587086A (en) * | 1991-09-05 | 1993-04-06 | Sanko Gosei Kk | Cylindrical impeller |
| CN1118843A (en) * | 1994-08-09 | 1996-03-20 | 东芝株式会社 | Transversly blowing fan |
| JP2001263285A (en) * | 2000-03-21 | 2001-09-26 | Mitsubishi Electric Corp | Thorough flow air blower and air conditioner |
| CN1914424A (en) * | 2004-09-30 | 2007-02-14 | 大金工业株式会社 | Impeller for blower and air conditioner having the same |
| CN102341601A (en) * | 2009-03-10 | 2012-02-01 | 大金工业株式会社 | Crossflow fan and air conditioner provided with same |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109538514A (en) * | 2019-01-21 | 2019-03-29 | 湖北工程职业学院 | A kind of crossflow fan of damping noise reduction |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2894345A1 (en) | 2015-07-15 |
| EP2894345A4 (en) | 2015-08-12 |
| WO2014038467A1 (en) | 2014-03-13 |
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Application publication date: 20150506 |