CN204900286U - Axial fan and air conditioner who has it - Google Patents

Abstract

The utility model discloses an axial flow fan and an indoor unit of an air conditioner with the same. The axial flow fan comprises: a casing, a first-stage movable impeller arranged in sequence in the flow direction of the wind, a second The first-stage stationary impeller, the second-stage moving impeller, and the second-stage stationary impeller, wherein the gap h1 between the first-stage moving impeller and the inner wall of the casing satisfies: 0.01L1≤h1≤0.02L1, where L1 is the first The blade length of the stage moving impeller and the gap h2 between the second stage moving impeller and the inner wall of the casing satisfy: 0.01L2≤h2≤0.02L2, where L2 is the blade length of the second stage moving impeller. According to the axial flow fan of the utility model, the total pressure and air supply distance of the axial flow fan can be effectively improved, and since the gap between each stage of the moving impeller and the inner wall of the casing is small, the axial flow fan can be reduced. The overall size makes the axial flow fan more suitable for installation in the indoor unit of the air conditioner, thereby optimizing the overall structure of the indoor unit of the air conditioner.

Description

Axial flow fan and air conditioner indoor unit having same

technical field

The utility model relates to the field of air conditioner equipment, in particular to an axial flow fan and an air conditioner indoor unit with the same.

Background technique

It is pointed out in the related art that the axial flow fan is generally only used on the outdoor unit of the air conditioner. The geometric shape and installation angle of each blade in the ordinary axial flow fan are the same and are evenly distributed on the hub, and the cross-sectional area of the blade from the root to the top gradually increases. The load on the blades is mainly concentrated on the middle and upper parts of the blades. Although this conventional forward-swept layout can effectively improve the aerodynamic performance of the axial flow fan, it cannot Not applicable, and the air supply distance of the axial flow fan cannot be guaranteed.

Utility model content

The utility model aims at at least solving one of the technical problems existing in the prior art. For this reason, the utility model is to provide an axial flow fan, the air volume of the axial flow fan is high, and the air supply distance is long.

The utility model also proposes an indoor unit of an air conditioner with the above-mentioned axial flow fan.

The axial flow fan according to the first aspect of the utility model includes: a casing and a first-stage moving impeller, a first-stage static impeller, a second-stage The moving impeller and the second-stage stationary impeller, wherein the gap h1 between the first-stage moving impeller and the inner wall of the casing satisfies: 0.01L1≤h1≤0.02L1, wherein L1 is the first-stage moving impeller The blade length of the impeller and the gap h2 between the second-stage moving impeller and the inner wall of the casing satisfy: 0.01L2≤h2≤0.02L2, wherein L2 is the blade length of the second-stage moving impeller.

According to the axial flow fan of the utility model, the total pressure and air supply distance of the axial flow fan can be effectively improved, and since the gap between each stage of the moving impeller and the inner wall of the casing is small, the axial flow fan can be reduced. The overall size makes the axial flow fan more suitable for installation in the indoor unit of the air conditioner, thereby optimizing the overall structure of the indoor unit of the air conditioner.

In some embodiments, the first-stage moving impeller is a meridional acceleration impeller, and the first-stage moving impeller includes a first moving hub formed in the shape of a truncated cone and a plurality of holes spaced apart in the circumferential direction of the first moving hub. the first moving blade, the blade length L1 of the first-stage moving impeller satisfies: L1=(D1-dm)/2, wherein, D1 is the outer diameter of the first-stage moving impeller, and dm is the first-stage moving impeller The average diameter of the moving hub, dm, satisfies: dm=(d1+d2)/2, wherein, d1 is the inlet diameter of the first moving hub, and d2 is the outlet diameter of the first moving hub.

In some embodiments, the cone angle α of the first moving hub satisfies: 15°≤α≤20°.

In some embodiments, the second-stage rotor includes a cylindrical second rotor hub and a plurality of second rotor blades spaced apart in the circumferential direction of the second rotor hub, the second-stage rotor The blade length L2 of the impeller satisfies: L2=(D2-d3)/2, wherein, D2 is the outer diameter of the second stage moving impeller, and d3 is the diameter of the second moving hub.

In some embodiments, the axial gap C1 between the blades of the first-stage moving impeller and the blades of the first-stage stationary impeller satisfies: C1=10%B1～15%B1, where B1 is the The axial chord length of the blades of the first stage moving impeller.

In some embodiments, the axial gap C2 between the blades of the second-stage moving impeller and the blades of the second-stage stationary impeller satisfies: C2=10%B2～15%B2, where B2 is the The axial chord length of the blades of the second stage moving impeller.

In some embodiments, the axial gap C3 between the blades of the first-stage stationary impeller and the blades of the second-stage moving impeller satisfies: C3≥50% B1, where B1 is the first-stage moving impeller The axial chord length of the blades of the impeller.

In some embodiments, at least one of the gap between the first-stage stationary impeller and the inner wall of the casing and the gap between the second-stage stationary impeller and the inner wall of the casing is 0 .

In some embodiments, the casing is formed in a cylindrical shape with equal cross-section, and the first stage moving impeller, the first stage stationary impeller, the second stage moving impeller and the second stage stationary impeller are the same Axially arranged in the casing.

The indoor unit of an air conditioner according to the second aspect of the utility model includes the axial flow fan according to the first aspect of the utility model.

According to the indoor unit of the air conditioner of the present utility model, the overall performance of the indoor unit of the air conditioner is improved by providing the axial flow fan of the first aspect.

Optionally, the indoor unit of the air conditioner is a cylindrical indoor vertical cabinet.

Additional aspects and advantages of the invention will be set forth in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.

Description of drawings

Fig. 1 is an exploded view of an axial flow fan according to an embodiment of the present invention;

Fig. 2 is an axial view of the axial flow fan shown in Fig. 1;

Fig. 3 is a sectional view along line A-A in Fig. 2;

Fig. 4 is a perspective view of a first-stage moving impeller according to an embodiment of the present invention;

Fig. 5 is a front view of the first stage moving impeller shown in Fig. 4;

Fig. 6 is a rear view of the first-stage moving impeller shown in Fig. 5;

Fig. 7 is a bottom view of the first stage moving impeller shown in Fig. 5;

Fig. 8 is a left view of the first-stage moving impeller shown in Fig. 5;

Fig. 9 is a sectional view along the line B-B in Fig. 5;

Fig. 10 is a perspective view of a second-stage moving impeller according to an embodiment of the present invention;

Fig. 11 is a front view of the second-stage impeller shown in Fig. 10;

Figure 12 is a rear view of the second-stage moving impeller shown in Figure 11;

Fig. 13 is a bottom view of the second-stage moving impeller shown in Fig. 11;

Fig. 14 is a left side view of the second-stage moving impeller shown in Fig. 11 .

Reference signs:

100: Axial fan;

1: chassis;

2: first stage moving impeller; 21: first moving blade; 22: first moving hub;

3: First stage stationary impeller; 31: First stationary blade; 32: First stationary hub;

4: second stage moving impeller; 41: second moving blade; 42: second moving hub;

5: second stage stationary impeller; 51: second stationary blade; 52: second stationary hub.

Detailed ways

Embodiments of the present invention are described in detail below, examples of which are shown in the drawings, wherein the same or similar reference numerals represent the same or similar elements or elements having the same or similar functions throughout. The embodiments described below by referring to the figures are exemplary and are intended to explain the present invention, but should not be construed as limiting the present invention.

The following disclosure provides many different embodiments or examples for realizing different structures of the present invention. To simplify the disclosure of the present invention, components and arrangements of specific examples are described below. Of course, they are only examples, and the purpose is not to limit the utility model. Furthermore, the present invention may repeat reference numerals and/or letters in different instances. This repetition is for the purpose of simplicity and clarity and does not in itself indicate a relationship between the various embodiments and/or arrangements discussed. In addition, various specific process and material examples are provided herein, but one of ordinary skill in the art will recognize the applicability of other processes and/or the use of other materials.

The following describes an axial flow fan 100 according to an embodiment of the present utility model with reference to FIGS. 1-14 . Specifically, the axial flow fan 100 can be used in an indoor unit of an air conditioner (not shown in the figure), especially can be used in a cylindrical indoor vertical cabinet machine (not shown in the figure). Other configurations of the indoor unit of the air conditioner according to the embodiment of the present invention, such as heat exchangers, etc., and operations are known to those skilled in the art, and will not be described in detail here.

As shown in Figures 1-3, the axial flow fan 100 according to the embodiment of the present invention includes: a casing 1, a first-stage moving impeller 2, a first-stage stationary impeller 3, a second-stage moving impeller 4 and a second Stage stationary impeller 5, first stage moving impeller 2, first stage stationary impeller 3, second stage moving impeller 4 and second stage stationary impeller 5 are all arranged in the casing 1 and arranged sequentially in the flow direction of the wind. For example, in the example of Fig. 3, the wind flows along the direction from right to left, the first stage moving blade wheel 2, the first stage static blade wheel 3, the second stage moving blade wheel 4 and the second stage static blade wheel 5 Arranged in sequence in the leftward direction, wherein, the first-stage moving impeller 2 and the second-stage moving impeller 4 are impellers that rotate relative to the casing 1, and the first-stage stationary impeller 3 and the second-stage stationary impeller 5 are relative to the Casing 1 is a static diffuser impeller.

In this way, since each stage of the impeller can do work on the airflow and provide a certain total pressure, compared with the single-stage axial flow fan, the total pressure is greater. Specifically, the total pressure value of the axial flow fan 100 can reach ordinary The total pressure value of the single-stage axial flow fan is more than twice that of the single-stage axial flow fan, and it overcomes the shortcoming of short air supply distance, while maintaining sufficient air volume and reducing the speed of the axial flow fan 100, and because of its extremely high working efficiency, it is compatible with Compared with the centrifugal fan under the air volume, the axial flow fan 100 has great performance advantages.

In addition, when the axial flow fan 100 is installed on the indoor unit of the air conditioner, compared with the conventional centrifugal air conditioner cabinet, the indoor unit of the air conditioner has higher efficiency and higher energy efficiency ratio. Next, the power of the axial flow fan is only 2/3 of the power of the centrifugal fan. Therefore, the two-stage axial flow fan 100 of the embodiment of the present invention, and the air conditioner indoor unit (especially the cylindrical indoor vertical cabinet machine) ) has obvious advantages compared with conventional air conditioner indoor cabinets.

Specifically, referring to Fig. 3, the gap h1 between the first-stage moving impeller 2 and the inner wall of the casing 1 satisfies: 0.01L1≤h1≤0.02L1, where L1 is the blade length of the first-stage moving impeller 2 (will be described below detailed in the text), the gap h2 between the second-stage moving impeller 4 and the inner wall of the casing 1 satisfies: 0.01L2≤h2≤0.02L2, where L2 is the blade length of the second-stage moving impeller 4 (will be detailed below described). Therefore, on the basis of considering the safety of falling, try to ensure that the gap is small enough, so as to ensure that the influence of the leakage flow is minimal, and the structural compactness of the axial flow fan 100 is improved.

In one embodiment of the present utility model, referring to Fig. 1 and Fig. 3, the casing 1 is formed into a cylindrical shape with equal section, the first stage moving impeller 2, the first stage static impeller 3, the second stage moving impeller 4 and the second stage The second-stage stationary impeller 5 is coaxially arranged in the casing 1. At this time, the gap h1 between the first-stage moving impeller 2 and the inner wall of the casing 1 refers to the distance between the outer diameter of the first-stage moving impeller 2 and the inner wall of the casing 1. One-half of the inner diameter difference of the shell 1, the gap h2 between the second-stage moving impeller 4 and the inner wall of the casing 1 refers to: the difference between the outer diameter of the second-stage moving impeller 4 and the inner diameter of the casing 1 one-half of.

Further preferably, at least one of the gap between the first-stage stationary impeller 3 and the inner wall of the casing 1 and the gap between the second-stage stationary impeller 5 and the inner wall of the casing 1 is zero. That is to say, the gap between the first-stage stationary impeller 3 and the inner wall of the casing 1 is 0, or the gap between the second-stage stationary impeller 5 and the inner wall of the casing 1 is 0, or the first-stage stationary impeller 3 While the gap between the second-stage stationary impeller 5 and the inner wall of the casing 1 is 0, the gap between the second-stage stationary impeller 5 and the inner wall of the casing 1 is also 0 (as shown in FIG. 3 ). In this way, the gap can be further ensured to be small enough, so as to ensure that the influence of leakage flow is minimal, and the structural compactness of the axial flow fan 100 is improved.

According to the axial flow fan 100 of the embodiment of the utility model, the total pressure and the air supply distance of the axial flow fan 100 can be effectively improved, and since the gap between the second stage moving impeller 4 and the inner wall of the casing 1 is small, the second stage The gap between the two-stage movable impeller 4 and the inner wall of the casing 1 is also small, thereby reducing the overall size of the axial flow fan 100, so that the axial flow fan 100 can be more suitable for being installed in an air conditioner indoor unit (especially a cylinder type indoor vertical cabinet machine), thereby optimizing the overall structure of the air conditioner indoor unit (especially the cylindrical indoor vertical cabinet machine).

According to a specific example of the present utility model, the axial fan 100 includes a two-stage structure, each stage includes a moving impeller and a stationary impeller, the moving impeller (rotatable impeller) of each stage is in front, and the stationary impeller (non-rotating) impeller) at the back, the casing 1 is formed into an equidiameter cylindrical structure that matches the air conditioner body size, and completely wraps the two-stage impeller structure. Wherein, referring to FIG. 1 , the first-stage moving impeller 2 includes a plurality of first moving blades 21 and a first moving hub 22, the plurality of first moving blades 21 are evenly spaced apart in the circumferential direction of the first moving hub 22, and the second The stage moving impeller 4 includes a plurality of second moving blades 41 and a second moving hub 42, the plurality of second moving blades 41 are evenly spaced apart in the circumferential direction of the second moving hub 42, and the first stage stationary impeller 3 includes a plurality of second moving hubs 42. A stator blade 31 and a first stator hub 32, a plurality of first stator blades 31 are evenly spaced apart in the circumferential direction of the first stator hub 32, and the second stage stator wheel 5 includes a plurality of second stator blades 51 and a second stator hub. The hub 52 , the plurality of second stationary blades 51 are evenly spaced apart in the circumferential direction of the second stationary hub 52 .

Preferably, at least one of the design parameters of the first-stage moving impeller 2 and the design parameters of the second-stage moving impeller 4 (such as blade length, axial chord length, number of blades, installation angle, etc.) is the same, and the first-stage static impeller The design parameters of 3 and at least one of the design parameters of the second-stage stationary impeller 5 (such as blade length, axial chord length, number of blades, installation angle, etc.) are the same. Further preferably, the structures of the first-stage stationary impeller 3 and the second-stage stationary impeller 5 are completely the same.

Therefore, when the two stages of moving impellers adopt the same design method and design parameters, and when the two stages of static impellers adopt the same design method and design parameters, it can be guaranteed that each stage works under the same working conditions, so that The working performance of the axial flow fan 100 is further improved, and the processing and manufacturing are facilitated, and the mold cost is reduced.

In one embodiment of the present utility model, with reference to Fig. 4-Fig. 9, the first-stage moving impeller 2 is a meridional acceleration impeller, and the first-stage moving impeller 2 includes a first moving impeller formed into a frustoconical shape (as shown in Fig. 9 ). The hub 22 and a plurality of first moving blades 21 spaced apart in the circumferential direction of the first moving hub 22 . Therefore, since the first-stage moving blade adopts a radially accelerated hub, the overall performance of the axial flow fan 100 can be further improved. Here, it should be noted that the concept of meridional acceleration should be well known to those skilled in the art, and will not be described in detail here.

Referring to Fig. 7, the blade length L1 of the first-stage moving impeller 2 is the average blade length, specifically, the blade length L1 of the first-stage moving impeller 2 satisfies: L1=(D1-dm)/2, wherein D1 is the first The outer diameter of the stage moving impeller 2, dm is the average diameter of the first moving hub 22, and dm satisfies: dm=(d1+d2)/2, wherein, d1 is the inlet diameter of the first moving hub 22, and d2 is the first moving hub 22. The outlet diameter of the hub 22. Optionally, according to the meridional acceleration ratio nf range of 0.9-1.3 and the axial chord length B1 (as shown in Figure 8 ) of the blade 21 of the first stage moving impeller 2, the optimal cone angle α( As shown in Figure 9) range, namely: 15°≤α≤20°. Here, it should be noted that the concept of the axial chord length should be well known to those skilled in the art, and will not be described in detail here.

In one embodiment of the present utility model, referring to FIGS. 10-14 , the second-stage moving impeller 4 includes a cylindrical second moving hub 42 and a plurality of first moving hubs 42 spaced apart in the circumferential direction. Two moving blades 41, at this time, referring to Fig. 13 and Fig. 14, the blade length L2 of the second stage moving impeller 4 satisfies: L2=(D2-d3)/2, wherein, D2 is the outer diameter of the second stage moving impeller 4 , d3 is the diameter of the second moving hub 42 .

Therefore, when the second-stage moving impeller 4 adopts an equal-diameter hub design, the smooth connection between the second-stage moving impeller 4 and the first-stage stationary impeller 3 can be ensured, thereby avoiding static and dynamic interference effects and clock effects, and further Reduced flow losses, forced vibration and noise.

In one embodiment of the present utility model, with reference to Fig. 3, the axial gap C1 between the blade 21 of the first stage moving impeller 2 and the blade 31 of the first stage stationary impeller 3 satisfies: C1=10% B1～15% B1, wherein, B1 is the axial chord length of the blade 21 of the first-stage impeller 2 . Thus, the interference effect of the moving impeller and the stationary impeller can be effectively avoided, and the compactness of the axial flow fan 100 can be improved, so as to better meet the size requirements of the indoor unit of the air conditioner.

In one embodiment of the present utility model, with reference to Fig. 3, the axial gap C2 between the blade 41 of the second-stage moving impeller 4 and the blade 51 of the second-stage stationary impeller 5 satisfies: C2=10% B2～15% B2, wherein, B2 is the axial chord length of the blade 41 of the second-stage impeller 4 . Thus, the interference effect of the moving impeller and the stationary impeller can be effectively avoided, and the compactness of the axial flow fan 100 can be improved, so as to better meet the size requirements of the indoor unit of the air conditioner.

In one embodiment of the present utility model, referring to FIG. 3 , the axial gap C3 between the blades 31 of the first-stage stationary impeller 3 and the blades 41 of the second-stage moving impeller 4 satisfies: C3≥50%B1, wherein, B1 is the axial chord length of the blade 21 of the first stage moving impeller 2 . Thus, the "clock" effect can be effectively avoided, and the compactness of the axial flow fan 100 can be effectively improved, so as to better meet the size requirements of the indoor unit of the air conditioner.

In the description of the present utility model, it should be understood that the orientations or positional relationships indicated by the terms "axial", "radial", and "circumferential" are based on the orientations or positional relationships shown in the drawings, and are only for It is convenient to describe the utility model and simplify the description, but not to indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation of the utility model.

In addition, the terms "first" and "second" are used for descriptive purposes only, and cannot be interpreted as indicating or implying relative importance or implicitly specifying the quantity of indicated technical features. Thus, a feature defined as "first" and "second" may explicitly or implicitly include one or more of these features. In the description of the present utility model, "plurality" means two or more, unless otherwise specifically defined.

In this utility model, unless otherwise specified and limited, terms such as "installation", "connection", "connection" and "fixation" should be understood in a broad sense, for example, it can be a fixed connection or a detachable connection. Connected, or integrated; it can be directly connected or indirectly connected through an intermediary, and it can be the internal communication of two elements or the interaction relationship between two elements. Those of ordinary skill in the art can understand the specific meanings of the above terms in the present utility model according to specific situations.

In the present invention, unless otherwise clearly specified and limited, the first feature may be in direct contact with the first feature or the first feature and the second feature through an intermediary indirect contact.

In the description of this specification, descriptions with reference to the terms "one embodiment", "some embodiments", "example", "specific examples", or "some examples" mean that specific features described in connection with the embodiment or example , structures, materials or features are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the described specific features, structures, materials or characteristics may be combined in any suitable manner in any one or more embodiments or examples. In addition, those skilled in the art can combine and combine different embodiments or examples and features of different embodiments or examples described in this specification without conflicting with each other.

Although the embodiments of the present invention have been shown and described, those skilled in the art can understand that various changes, modifications, substitutions and modifications, the scope of the present invention is defined by the claims and their equivalents.

Claims (11)

1. an axial-flow blower, is characterized in that, comprising: casing and being located in described casing and the first order movable vane of arranging successively on the flow direction of wind wheel, first stage stator blades wheel, second level movable vane wheel and second level stationary blade wheel, wherein,

Gap h1 between described first order movable vane wheel and the inwall of described casing meets: 0.01L1≤h1≤0.02L1, and wherein, L1 is the length of blade of described first order movable vane wheel,

Gap h2 between described second level movable vane wheel and the inwall of described casing meets: 0.01L2≤h2≤0.02L2, and wherein, L2 is the length of blade of described second level movable vane wheel.

2. axial-flow blower according to claim 1, it is characterized in that, described first order movable vane wheel is meridian acceleration impeller, and described first order movable vane wheel comprises the first runner hub of being formed as frustoconic shape and isolated multiple first moving vane in the circumference of described first runner hub

The length of blade L1 of described first order movable vane wheel meets: L1=(D1-dm)/2, wherein, D1 is the external diameter of described first order movable vane wheel, dm is the average diameter of described first runner hub, dm meets: dm=(d1+d2)/2, wherein, d1 is the inlet diameter of described first runner hub, and d2 is the outlet diameter of described first runner hub.

3. axial-flow blower according to claim 2, is characterized in that, the cone angle alpha of described first runner hub meets: 15 °≤α≤20 °.

4. axial-flow blower according to claim 1, is characterized in that, described second level movable vane is taken turns to comprise and is formed as columniform second runner hub and isolated multiple second moving vane in the circumference of described second runner hub,

The length of blade L2 of described second level movable vane wheel meets: L2=(D2-d3)/2, and wherein, D2 is the external diameter of described second level movable vane wheel, and d3 is the diameter of described second runner hub.

5. axial-flow blower according to claim 1, it is characterized in that, axial clearance C1 between the blade of described first order movable vane wheel and the blade of described first stage stator blades wheel meets: C1=10%B1 ~ 15%B1, and wherein, B1 is the axial chord length of the described blade of described first order movable vane wheel.

6. axial-flow blower according to claim 1, it is characterized in that, axial clearance C2 between the blade of described second level movable vane wheel and the blade of described second level stationary blade wheel meets: C2=10%B2 ~ 15%B2, and wherein, B2 is the axial chord length of the described blade of described second level movable vane wheel.

7. axial-flow blower according to claim 1, it is characterized in that, axial clearance C3 between the blade of described first stage stator blades wheel and the blade of described second level movable vane wheel meets: C3 >=50%B1, and wherein, B1 is the axial chord length of the blade of described first order movable vane wheel.

8. axial-flow blower according to claim 1, is characterized in that, one, at least gap in the gap between described first stage stator blades wheel with the inwall of described casing and the gap between the inwall of described second level stationary blade wheel and described casing is 0.

9. axial-flow blower according to claim 1, it is characterized in that, described casing is formed as uniform section cylindrical shape, and described first order movable vane wheel, described first stage stator blades wheel, described second level movable vane wheel and described second level stationary blade wheel are located in described casing coaxially.

10. an air conditioner indoor machine, is characterized in that, comprises the axial-flow blower according to any one of claim 1-9.

11. air conditioner indoor machines according to claim 10, is characterized in that, described air conditioner indoor machine is cylinder type indoor vertical cabinet-type air conditioner.