CN217481585U - Mounting structure of through-flow fan blade, wall-mounted indoor unit and air conditioner - Google Patents

Abstract

The utility model provides a mounting structure and hanging indoor unit, air conditioner of through-flow fan blade, mounting structure includes and lies in snail tongue, the backplate that sets up respectively at impeller positive, back of the body two sides in the indoor unit, the impeller includes end plate, blade, the blade with the backplate, the minimum interval between the snail tongue is S3, S4 respectively, then the backplate just has seted up first slot to the second backplate portion of end plate, the minimum interval of first slot with the end plate is S3; and/or the second volute tongue part of the volute tongue, which is right opposite to the end plate, is provided with a second groove, and the minimum distance between the second groove and the end plate is S4. Through a mounting structure and hanging interior machine, air conditioner of through-flow fan blade on the basis that reduces through-flow fan blade turbulent flow phenomenon and turbulent flow noise, improve the impeller to the air-out quality of air current and/or the formation quality of its inside circulation whirlpool, the amount of wind, efficiency and the noise control of high-efficient guarantee through-flow fan blade.

Description

Mounting structure of through-flow fan blade, wall-mounted indoor unit and air conditioner

Technical Field

The utility model relates to an air conditioning technology field particularly, relates to a mounting structure and hanging interior machine, air conditioner of through-flow fan blade.

Background

In a wall-mounted indoor unit of an air conditioner, as shown in fig. 1 to 4, a heat exchanger 2 located in an upper air duct and a tubular impeller 3 located in a lower air duct are respectively arranged in the indoor unit 1, a back plate 4 in a vortex shape is arranged on the back of the impeller 3, and a volute tongue 5 is arranged on the front of the impeller 3. The minimum distance S1 between the impeller 3 and the back plate 4 determines the airflow outlet direction of the impeller 3; the minimum distance S2 between the impeller 3 and the volute tongue 5 has a great influence on the stability of the circulating vortex 13 formed inside the impeller 3 and continuously approaching the volute tongue 5.

In the prior art, the impeller 3 is composed of a plurality of blades 10 connected in the axial direction, wherein the blades 10 are composed of a plurality of blades 9 attached to one side of an end plate 8, the end plate 8 is in a disc shape or a circular ring shape, and the outer diameter D0 is larger than the outer diameter D2 of the blades 9. Therefore, the airflow of the impeller 3 is actually divided into two parts corresponding to the end plate 8 and the blades 9, the two air flows have different flowing directions and are easy to interfere with each other to cause turbulence, so that the air volume and the efficiency of the cross-flow fan blade are low, and large turbulence noise is generated. In addition, the air flow outlet direction of the impeller 3 and the stability of the circulating vortex 13 are not ideal, which further affects the air volume, efficiency and noise of the cross-flow fan.

SUMMERY OF THE UTILITY MODEL

In view of this, the technical problem to be solved by the present invention is: the first aspect is to provide a mounting structure of a cross-flow fan blade, which improves the air outlet quality of an impeller to airflow and/or the formation quality of an internal circulating vortex of the impeller on the basis of reducing the turbulence phenomenon and the turbulence noise of the cross-flow fan blade, and efficiently ensures the air quantity, efficiency and noise control of the cross-flow fan blade.

For solving above-mentioned first aspect technical problem, the utility model provides a mounting structure of through-flow fan blade, include and lie in snail tongue, the backplate that the impeller just, back of the body two sides set up respectively in the built-in machine, the impeller includes end plate, blade, the blade with the backplate minimum interval between the snail tongue is S3, S4 respectively, then:

the back plate is provided with a first groove opposite to the second back plate part of the end plate, and the minimum distance between the first groove and the end plate is S3;

and/or the second volute tongue part of the volute tongue, which is right opposite to the end plate, is provided with a second groove, and the minimum distance between the second groove and the end plate is S4.

Through-flow fan's mounting structure, on the basis that reduces through-flow fan turbulent flow phenomenon and turbulent noise, improve the impeller to the air-out quality of air current and/or its inside circulating vortex's formation quality, the amount of wind, efficiency and the noise control of high-efficient guarantee through-flow fan.

Preferably, the back plate is a vortex-shaped structure further including a first back plate portion and a third back plate portion, the first back plate portion faces the vane and is arranged in a staggered manner with the second back plate portion, the third back plate portion extends in a downward vortex manner along a side close to the inner outlet portion, and the first groove has a concave cross section and smoothly transitions with the third back plate portion.

The appropriate deceleration of the fluid B between the end plate and the back plate at the second back plate portion can be sufficiently satisfied, and the smooth formation of confluence at the third back plate portion with the main fluid from the first back plate portion can be ensured.

Preferably, the third backplate portion comprises:

a third main plate portion extending from the first back plate portion;

a third auxiliary plate portion extending from the second back plate portion;

the third auxiliary plate part is arranged in an inward convex shape compared with the third main plate part, and the convex height H1 is arranged in a gradually enlarged manner along the extending direction of the third back plate part.

The expansion rate of the diffusion section of the fluid B during confluence can be reduced, so that the rapid speed reduction of the fluid B is avoided, the occurrence of turbulent flow is reduced as much as possible, and the deterioration of the static pressure recovery efficiency of the diffusion section of the air outlet of the internal machine is inhibited.

Preferably, the maximum projection width of the third auxiliary plate part is K4, and K4/K1 is 1-1.5, wherein K1 is the width of the first groove.

The flow area of the fluid B in the merging process can be sufficiently covered, and the smooth merging with the main fluid from the third main plate part can be ensured.

Preferably, the volute tongue further comprises a first volute tongue portion and a third volute tongue portion, the first volute tongue portion faces the blade and is arranged in a staggered mode with the second volute tongue portion, the third volute tongue portion extends along one side close to the inner machine outlet portion, and the second groove is of a concave cross section and is in smooth transition with the third volute tongue portion.

The proper deceleration of the fluid C between the end plate and the volute tongue at the second volute tongue part can be fully met, and the smooth confluence of the main fluid from the first volute tongue part and the main fluid at the third volute tongue part can be ensured.

Preferably, the third volute tongue comprises:

the third main tongue part correspondingly extends from the first volute tongue part;

the third auxiliary tongue part correspondingly extends from the second volute tongue part;

the third auxiliary tongue portion is arranged in an inward convex shape compared with the third main tongue portion, and the convex height H2 is arranged in a gradually enlarged manner along the extending direction of the third volute tongue portion.

The expansion rate of the diffusion section of the fluid C during confluence can be reduced, so that the rapid speed reduction of the fluid C is avoided, the occurrence of turbulence is reduced as much as possible, and the aerodynamic performance deterioration of air flow outlet of an internal machine is prevented as much as possible.

Preferably, the maximum height difference of H2 is Δ H2, and Δ H2/H4 is 1-2, wherein H4 is the groove depth of the second groove.

When Δ H2/H4 is 1-2, the convex setting effect of the third volute tongue portion is better.

Preferably, the width of the first groove is K1, the width of the second groove is K2, and the thickness of the end plate is K3, so that K1/K3 is 1.5-3 and/or K2/K3 is 1.5-3.

For example, K1/K3 is 1.5 to 3, which can sufficiently cover the range of the flow field of the fluid B and hardly interfere with the main fluid from the first back plate portion. Similarly, when K2/K3 is 1.5 to 3, the flow field range of the fluid C is sufficiently covered, and interference with the primary fluid from the first volute tongue portion is hardly generated.

The to-be-solved technical problem of the utility model is still in: the second aspect provides a wall-mounted indoor unit, and/or the third aspect provides an air conditioner, which improves the quality of the air outlet of the impeller to the airflow and/or the quality of the formed internal circulating vortex of the impeller on the basis of reducing the turbulence phenomenon of the cross-flow fan blade and the turbulence noise thereof, and efficiently ensures the air volume, efficiency and noise control of the cross-flow fan blade.

For solving the technical problem of above-mentioned second aspect, the utility model provides a hanging interior unit has the arbitrary embodiment of first aspect the mounting structure of through-flow fan blade.

In order to solve the technical problem of the third aspect, the utility model provides an air conditioner has the mounting structure of any embodiment of the first aspect through-flow fan blade.

Compared with the prior art, a mounting structure and hanging interior unit, air conditioner of through-flow fan blade have following beneficial effect:

1) on the basis of reducing the turbulence phenomenon and the turbulence noise of the cross-flow fan blade, the air outlet quality of the impeller to the air flow and/or the forming quality of the internal circulating vortex of the impeller are improved, and the air quantity, the efficiency and the noise control of the cross-flow fan blade are efficiently ensured;

2) the expansion rate of the diffusion section of the fluid between the end plate and the back plate can be reduced when the fluid is converged, so that the rapid speed reduction of the fluid is avoided, the occurrence of turbulence is reduced as much as possible, and the deterioration of the static pressure recovery efficiency of the diffusion section at the air outlet of the internal machine is inhibited;

3) the expansion rate of the diffusion section of the fluid between the end plate and the volute tongue can be reduced when the fluid is converged, so that the rapid speed reduction of the fluid is avoided, the occurrence of turbulence is reduced as much as possible, and the aerodynamic performance deterioration of the air flow outlet of the internal machine is prevented as much as possible.

Drawings

Some of the figures that make up the present invention are intended to provide a further understanding of the invention, and the illustrative embodiments and descriptions thereof are intended to explain the present invention and not to constitute an undue limitation on the invention. In the drawings:

fig. 1 is a schematic view of an installation structure of a wall-mounted indoor unit in the background art of the present invention;

fig. 2 is a schematic perspective view of an impeller according to the present invention;

fig. 3 is a schematic perspective view of a blade body according to the present invention;

FIG. 4 is a partially enlarged schematic view of FIG. 1;

fig. 5 is a schematic view of a first mounting structure of a back plate in a wall-mounted internal unit according to embodiment 1 of the present invention;

fig. 6 is a schematic view of a second mounting structure of a back plate in a wall-mounted internal unit according to embodiment 1 of the present invention;

fig. 7 is a schematic view of a first mounting structure of a volute tongue in a wall-mounted internal unit according to embodiment 1 of the present invention;

fig. 8 is a schematic view of a second mounting structure of a volute tongue in a wall-mounted internal unit according to embodiment 1 of the present invention;

fig. 9 is a schematic plan view of a cross-flow fan blade mounting structure according to embodiment 1 of the present invention;

fig. 10 is a schematic view of a third mounting structure of another back plate in a wall-mounted indoor unit according to embodiment 2 of the present invention;

fig. 11 is a schematic view of a third mounting structure of another volute tongue in a wall-mounted indoor unit according to embodiment 2 of the present invention;

fig. 12 is a schematic plan view of another cross-flow fan blade mounting structure according to embodiment 2 of the present invention.

Description of reference numerals:

1-inner machine, 2-heat exchanger, 3-impeller, 4-back plate, 401-first back plate portion, 402-second back plate portion, 403-third back plate portion, 4031-third main plate portion, 4032-third auxiliary plate portion, 5-volute tongue, 501-first volute tongue portion, 502-second volute tongue portion, 503-third volute tongue portion, 5031-third main tongue portion, 5032-third auxiliary tongue portion, 6-wind deflector, 7-face plate, 8-end plate, 9-blade, 10-blade body, 11-first groove, 12-second groove, 13-circulating vortex.

Detailed Description

In order to make the above objects, technical solutions and advantages of the present invention more clearly understood, the present invention will be further described in detail with reference to the accompanying drawings and embodiments. It is to be understood that the specific embodiments of the invention described herein constitute only some of the embodiments of the invention, and are intended only to illustrate the invention, and not to limit the invention, in which case the features of the embodiments and examples may be combined with each other without conflict.

Example 1

Referring to fig. 1-9, the utility model provides a mounting structure of through-flow fan blade, include and lie in volute tongue 5, backplate 4 that impeller 3 just, back of the body both sides set up respectively in indoor unit 1, impeller 3 includes end plate 8, blade 9 with backplate 4 minimum interval between the volute tongue 5 is S3, S4 respectively, then:

the back plate 4 is opened with a first groove 11 opposite to the second back plate part 402 of the end plate 8, and the minimum distance between the first groove 11 and the end plate 8 is S3;

and/or the volute tongue 5 is provided with a second groove 12 opposite to the second volute tongue portion 502 of the end plate 8, and the minimum distance between the second groove 12 and the end plate 8 is S4.

Specifically, as described in the background of the invention, the outer diameter D0 of the end plate 8 is larger than the outer diameter D2 of the blade 9 because the blade bodies 10 are generally formed by injection molding, and the blade bodies 10 are ultrasonically welded to form the impeller 3. In order to ensure the resin flow stability of the vane body 10 at the time of injection molding, the assembly accuracy at the time of ultrasonic welding and to ensure margin, while preventing the blade 9 from being damaged when dropped, D0 must be larger than D2. In the ultrasonic welding process, the plurality of fan blade bodies 10 are respectively connected in a staggered manner according to a certain angle by taking the rotating shaft of the impeller 3 as the center, so that the axial pressure variation of the impeller 3 keeps a certain phase; of course, in the injection molding process of the blade body 10, the plurality of blades 9 are also arranged at unequal intervals, so that the problem of noise of the cross-flow blade can be greatly improved, especially the rotating noise caused by the pressure variation of the rotation of the blades 9.

However, in view of the assembly accuracy of the impeller 3, the minimum spacing between the impeller 3 and the back plate 4 is only the minimum spacing between the end plate 8 and the back plate 4, herein collectively denoted as S1, which is smaller than the minimum spacing S3 between the blades 9 and the back plate 4; similarly, the minimum distance between the impeller 3 and the volute tongue 5 is only the minimum distance between the end plate 8 and the volute tongue 5, and is herein collectively denoted as S2, which is smaller than the minimum distance S4 between the blade 9 and the volute tongue 5. Therefore, in the prior art, the airflow outlet direction of the impeller 3 and the stability of the circulating vortex 13 are generally not ideal, and the reason for this is that D0 > D2: the minimum spacing between the blades 9 and the back plate 4 and/or the volute tongue 5 is generally not at the optimum theoretical spacing, but rather is at a greater radius.

In the present invention, taking the opening of the first groove 11 as an example, the back plate 4 can be divided into a first back plate portion 401 facing the blade 9 and a second back plate portion 402 facing the end plate 8. At the second back plate portion 402, due to the opening of the first grooves 11, the minimum distance S1 between the end plate 8 and the back plate 4 (i.e. the second back plate portion 402) will be consistent with the minimum distance S3 between the blades 9 and the back plate 4 (i.e. the first back plate portion 401). Furthermore, even if the airflow of the impeller 3 is forced to be divided into two parts because D0 is greater than D2, the fluid B between the end plate 8 and the back plate 4 is properly decelerated when flowing through the first groove 11, so that the fluid B can smoothly form confluence with a main fluid from the blades 9 and the back plate 4, and thus the two parts of fluid are ensured not to interfere with each other to cause turbulence, and further the turbulence phenomenon of the cross-flow fan and the turbulence noise thereof are effectively reduced; secondly, when the impeller 3 is assembled in the internal machine 1, the minimum distance S1 between the end plate 8 and the back plate 4 (i.e., the second back plate 402) is used as a control reference, so that the minimum distance S3 between the blades 9 and the back plate 4 is effectively ensured to be the optimal theoretical distance S1, and further, under the action of the spiral structure of the back plate 4, the air flow outlet direction of the impeller 3 can be effectively induced in the static pressure recovery direction.

Similarly, taking the opening of the second groove 12 as an example, the volute tongue 5 can be divided into a first volute tongue portion 501 facing the blade 9 and a second volute tongue portion 502 facing the end plate 8. At the second volute tongue portion 502, due to the opening of the second groove 12, the minimum distance S2 between the end plate 8 and the volute tongue 5 (i.e. the second volute tongue portion 502) is consistent with the minimum distance S4 between the blade 9 and the volute tongue 5 (i.e. the first volute tongue portion 501). Furthermore, even if the airflow of the impeller 3 is forced to be divided into two flows because D0 is greater than D2, the flow C between the end plate 8 and the volute tongue 5 is properly decelerated when flowing through the second groove 12, so that the flow C can smoothly form confluence with a main fluid from the blade 9 and the volute tongue 5, and thus the two flows are ensured not to interfere with each other to cause turbulence, and further the turbulence phenomenon of the cross-flow fan and the turbulence noise thereof are effectively reduced; secondly, when the impeller 3 is assembled in the internal machine 1, the minimum distance S2 between the end plate 8 and the volute tongue 5 (i.e. the second volute tongue portion 502) is used as a control reference, so that the minimum distance S4 between the blade 9 and the volute tongue 5 is effectively ensured to be the optimal theoretical distance S2, and the circulating vortex 13 formed in the impeller 3 is ensured to be stable and to meet the ideal state.

To sum up, through-flow fan's mounting structure, on the basis that reduces through-flow fan blade turbulent phenomenon and turbulent noise thereof, improve the impeller to the air-out quality of air current and/or the formation quality of its inside circulation whirlpool, the amount of wind, efficiency and the noise control of high-efficient guarantee through-flow fan blade.

Preferably, the back plate 4 is a vortex-shaped structure further including a first back plate portion 401 and a third back plate portion 403, the first back plate portion 401 is opposite to the vane 9 and is arranged in a staggered manner with the second back plate portion 402, the third back plate portion 403 extends along a side close to the outlet of the inner machine 1 in a downward vortex shape, and the first groove 11 has a concave cross section and smoothly transitions with the third back plate portion 403.

Specifically, the fluid B is appropriately decelerated while flowing through the first grooves 11, and then continues to flow through the third back plate portion 403 to merge with the main fluid from between the blades 9 and the first back plate portion 401. The first grooves 11 have a concave cross section and smoothly transition with the third back plate portion 403, which can sufficiently satisfy the appropriate deceleration of the fluid B at the second back plate portion 402 and ensure smooth confluence with the main fluid from the first back plate portion 401 at the third back plate portion 403. Then, the merged air flow can be guided to the indoor through the air deflector 6, wherein the air deflector 6 is arranged at the outlet part of the indoor unit 1, namely the air outlet side below the impeller 3.

Preferably, the volute tongue 5 further comprises a first volute tongue portion 501 and a third volute tongue portion 503, the first volute tongue portion 501 faces the blade 9 and is arranged in a staggered manner with the second volute tongue portion 502, the third volute tongue portion 503 extends along a side close to the outlet of the inner machine 1, and the second groove 12 is concave in cross section and smoothly transits to the third volute tongue portion 503.

Specifically, a panel 7 is arranged right in front of the heat exchanger 2, and the volute tongue 5 is integrally positioned at the lower rear part of the panel 7. The fluid C is suitably decelerated as it flows through the second grooves 12 and then continues to flow past the third volute tongue 503 to merge with the primary fluid from between the vanes 9 and the first volute tongue 501. The second groove 12 has a concave cross section and smoothly transitions to the third tongue portion 503, so that the fluid C can be adequately decelerated at the second tongue portion 502, and a smooth confluence with the main fluid from the first tongue portion 501 at the third tongue portion 503 can be ensured. The combined air flow can then be guided to the room by the air deflector 6.

Preferably, the width of the first groove 11 is K1, the width of the second groove 12 is K2, and the thickness of the end plate 8 is K3, so that K1/K3 is 1.5 to 3 and/or K2/K3 is 1.5 to 3.

Specifically, K1 and K2 may be equal or unequal, and may be specifically set as required. For example, K1/K3 is 1.5 to 3, which can sufficiently cover the range of the flow field of the fluid B and hardly interfere with the primary fluid from the first back plate 401. Similarly, when K2/K3 is 1.5 to 3, the flow field range of the fluid C is sufficiently covered, and interference with the primary fluid from the first volute tongue portion 501 is hardly generated.

Example 2

Preferably, referring to fig. 10-12, the third back plate portion 403 comprises:

a third main plate portion 4031 extending from the first back plate portion 401;

a third auxiliary plate portion 4032 extending from the second back plate portion 402;

the third auxiliary plate portion 4032 is provided in a convex shape inward from the third main plate portion 4031, and the protrusion height H1 is gradually enlarged in the extending direction of the third back plate portion 403.

Specifically, since the end plate 8 has no vanes 9 in the vicinity thereof, the radial flow which does not coincide with the flow outlet direction of the outer periphery of the vanes 9 is reduced, that is, the air volume of the third auxiliary plate 4032 is smaller than that of the third main plate 4031. As described in embodiment 1, the fluid B is first decelerated at the first grooves 11, and then flows through the third auxiliary plate 4032 at the third back plate 403 with a small air volume to join with a large air volume from the third main plate 4031. In this case, the provision of the projection on the third auxiliary plate 4032 can reduce the expansion rate of the diffuser of the fluid B at the time of confluence, thereby avoiding a rapid deceleration of the fluid B, minimizing the occurrence of turbulence, and suppressing deterioration of the static pressure recovery efficiency of the diffuser at the outlet of the inner machine 1.

Preferably, the third volute tongue portion 503 includes:

a third main tongue 5031 extending from the first volute tongue 501;

a third secondary tongue 5032 extending from the second tongue 502;

the third auxiliary tongue portion 5032 is provided to be inwardly convex compared to the third main tongue portion 5031, and the convex height H2 is gradually enlarged along the extending direction of the third volute tongue portion 503.

Specifically, since the end plate 8 has no vanes 9 in the vicinity thereof, the radial flow that does not coincide with the direction of the airflow outlet at the outer periphery of the vanes 9 is reduced, that is, the air volume of the third main tongue 5031 is smaller than that of the third sub tongue 5032. As described in embodiment 1, the fluid C first decelerates at the second grooves 12 and then flows through the third auxiliary tongue 5032 with a small air flow at the third volute tongue 503 to merge with the large air flow from the third main tongue 5031. At this time, the protrusion of the third auxiliary tongue 5032 reduces the expansion rate of the diffuser when the fluid C merges, thereby avoiding a rapid deceleration of the fluid C, reducing the occurrence of turbulence as much as possible, and preventing the aerodynamic performance of the air flow of the inner machine 1 from deteriorating as much as possible.

Preferably, when the maximum protrusion width of the third auxiliary plate 4032 is K4 and the maximum protrusion width of the third auxiliary tongue 5032 is K5, K4/K1 is 1 to 1.5 and/or K5/K2 is 1 to 1.5.

Specifically, the width of the projection of the third auxiliary plate 4032 may be set to be constant or variable so as to be equal to the width of K1, or may be set to be variable so as to be different from the width of K1, and may be specifically set as needed. Taking 1 < K4/K1 ≦ 1.5 as an example, the protrusion width of the third auxiliary plate 4032 may also be gradually enlarged along the extending direction of the third back plate 403, and in this case, the maximum protrusion width K4 corresponds to the extending end of the third auxiliary plate 4032. This can sufficiently cover the flow field range of the fluid B during the joining process, and can ensure smooth joining with the main fluid from the third main plate 4031.

Similarly, the protrusion width of the third auxiliary tongue 5032 may be a fixed value and set to be equal to the width of K2, or a variable value and set to be different from the width of K2, and may be specifically set as required. Taking 1 < K5/K2 ≤ 1.5 as an example, the protrusion width of the third auxiliary tongue 5032 can also be gradually enlarged along the extending direction of the third volute tongue 503, and at this time, the maximum protrusion width K5 corresponds to the extending end of the third auxiliary tongue 5032. This can sufficiently cover the range of the flow field of the fluid C during the joining process, and ensure smooth joining with the primary fluid from the third main tongue 5031.

Preferably, the maximum height difference of H1 is Δ H1, and the maximum height difference of H2 is Δ H2, then:

the groove depth of the first groove 11 is H3, and the delta H1/H3 is 1-2;

and/or the groove depth of the second groove 12 is H4, and the delta H2/H4 is 1-2.

Specifically, the extension length of the third back plate 403 is substantially longer than that of the second back plate 402, and the range of the flow field of the fluid B in the merging process is larger than that of the fluid B flowing through the first grooves 11, and when Δ H1/H3 is 1-2, the convex setting effect of the third auxiliary plate 4032 is better.

Similarly, the extension length of the third volute tongue portion 503 is substantially longer than that of the second volute tongue portion 502, and the range of the flow field of the fluid C during the merging process is larger than that of the fluid C flowing through the second groove 12, so that when Δ H2/H4 is 1-2, the convex setting effect of the third volute tongue portion 5032 is better.

Example 3

The utility model also provides a hanging indoor unit, have any embodiment in embodiment 1-2 the mounting structure of through-flow fan blade.

The utility model also provides an air conditioner, have embodiment 1-2 in any embodiment the mounting structure of through-flow fan blade.

Specifically, it can be understood by those skilled in the art that, when the wall-mounted indoor unit and/or the air conditioner provided in embodiment 3 has the installation structure of the cross-flow fan blade described in any one of embodiments 1 to 2, the solution of the corresponding technical problem and the achievement of the technical effect thereof can be referred to the description of the installation structure of the cross-flow fan blade in embodiments 1 to 2, and details are not repeated here.

Although the present invention is disclosed above, the present invention is not limited thereto. Various changes and modifications may be effected by one skilled in the art without departing from the spirit and scope of the invention, as defined in the appended claims.

Claims (10)

1. The utility model provides a mounting structure of through-flow fan blade, characterized in that includes and lies in volute tongue (5), backplate (4) that impeller (3) just, back of the body both sides set up respectively in indoor set (1), impeller (3) include end plate (8), blade (9), the minimum interval between blade (9) and backplate (4), volute tongue (5) is S3, S4 respectively, then:

the back plate (4) is provided with a first groove (11) opposite to the second back plate part (402) of the end plate (8), and the minimum distance between the first groove (11) and the end plate (8) is S3;

and/or the volute tongue (5) is provided with a second groove (12) opposite to a second volute tongue part (502) of the end plate (8), and the minimum distance between the second groove (12) and the end plate (8) is S4.

2. A cross-flow fan blade mounting structure according to claim 1, wherein the back plate (4) is a vortex-shaped structure further comprising a first back plate portion (401) and a third back plate portion (403), the first back plate portion (401) faces the blades (9) and is arranged in a staggered manner with the second back plate portion (402), the third back plate portion (403) extends in a downward vortex shape along a side close to the outlet portion of the inner machine (1), and the first groove (11) has a concave cross section and is in smooth transition with the third back plate portion (403).

3. A mounting structure for a through-flow fan blade according to claim 2, characterised in that the third backplate portion (403) comprises:

a third main plate portion 4031 extending from the first back plate portion 401 in a corresponding manner;

a third auxiliary plate portion 4032 extending from the second back plate portion 402 in a corresponding manner;

the third auxiliary plate portion 4032 is provided in a convex shape inward in comparison with the third main plate portion 4031, and the convex height H1 is enlarged in a gradual manner in the extending direction of the third back plate portion 403.

4. The cross-flow fan blade mounting structure according to claim 3, wherein the maximum projection width of the third auxiliary plate part (4032) is K4, so that K4/K1 is 1-1.5, where K1 is the width of the first groove (11).

5. A cross-flow fan blade mounting structure according to claim 1, wherein the volute tongue (5) further comprises a first volute tongue portion (501) and a third volute tongue portion (503), the first volute tongue portion (501) faces the blade (9) and is staggered with the second volute tongue portion (502), the third volute tongue portion (503) extends along a side close to the outlet of the inner unit (1), and the second groove (12) has a concave cross section and is in smooth transition with the third volute tongue portion (503).

6. A cross-flow fan blade mounting structure according to claim 5, wherein the third volute tongue part (503) comprises:

a third main tongue portion (5031) extending from the first volute tongue portion (501);

a third auxiliary tongue portion (5032) extending from the second volute tongue portion (502);

the third auxiliary tongue portion (5032) is provided to be convex inward compared to the third main tongue portion (5031), and the convex height H2 is gradually enlarged in the extending direction of the third volute tongue portion (503).

7. The cross-flow fan blade mounting structure according to claim 6, wherein the maximum height difference of H2 is Δ H2, and Δ H2/H4 is 1-2, wherein H4 is the groove depth of the second groove (12).

8. The mounting structure of the cross-flow fan blade according to any one of claims 1 to 7, wherein the width of the first groove (11) is K1, the width of the second groove (12) is K2, and the thickness of the end plate (8) is K3, so that K1/K3 is 1.5-3 and/or K2/K3 is 1.5-3.

9. A wall-mounted indoor unit, characterized in that the wall-mounted indoor unit is provided with a mounting structure of the cross-flow fan blade as set forth in any one of claims 1 to 8.

10. An air conditioner characterized in that the air conditioner has a mounting structure of the cross-flow fan blade according to any one of claims 1 to 8.

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