A cross-flow fan mounting structure and a wall-mounted indoor unit and an air conditioner

Abstract

The application provides a kind of installation structure of cross-flow fan blade and wall hanging inner machine, air conditioner, the installation structure includes the volute tongue and back plate respectively arranged in inner machine at the front and back of impeller, the impeller includes end plate, blade, the minimum spacing between the blade and the back plate, the volute tongue is S3, S4 respectively, then: the second back plate part of the back plate is opened to the first groove for the end plate, the minimum spacing between the first groove and the end plate is S3, and / or the second volute tongue part of the volute tongue is opened to the second groove for the end plate, the minimum spacing between the second groove and the end plate is S4. Through the installation structure of cross-flow fan blade and wall hanging inner machine, air conditioner provided by the application, on the basis of reducing cross-flow fan blade turbulence phenomenon and its turbulence noise, the air outlet quality of impeller for airflow and / or the formation quality of its internal circulation vortex are improved, the air volume, efficiency and noise control of cross-flow fan blade are efficiently guaranteed.

Description

Technical Field

[0001] This invention relates to the field of air conditioning technology, and more specifically, to an installation structure for a cross-flow fan blade and a wall-mounted indoor unit and air conditioner. Background Technology

[0002] In the wall-mounted indoor unit of the air conditioner, see Figure 1-4 As shown, the indoor unit 1 is equipped with a heat exchanger 2 located in the upper air duct and a cross-flow impeller 3 located in the lower air duct. A vortex-shaped back plate 4 is provided on the back of the impeller 3, and a volute tongue 5 is provided on the front of the impeller 3. The minimum distance S1 between the impeller 3 and the back plate 4 determines the airflow direction of the impeller 3; the minimum distance S2 between the impeller 3 and the volute tongue 5 has a significant impact on the stability of the circulating vortex 13 formed inside the impeller 3 and continuously approaching the volute tongue 5.

[0003] In the prior art, the impeller 3 is composed of multiple axially connected blades 10, each blade 10 consisting of multiple blades 9 mounted on one side of the end plate 8. The end plate 8 is circular or annular, and its outer diameter D0 is larger than the outer diameter D2 of the blades 9. Consequently, corresponding to the end plate 8 and the blades 9, the airflow of the impeller 3 is actually divided into two streams. The flow directions of these two streams are inconsistent, easily interfering with each other and causing turbulence. This not only leads to low airflow and efficiency of the cross-flow fan but also generates significant turbulent noise. Furthermore, the airflow outlet direction of the impeller 3 and the stability of the circulating vortex 13 are usually not ideal, further affecting the airflow, efficiency, and noise of the cross-flow fan. Summary of the Invention

[0004] In view of this, the technical problem to be solved by the present invention is: firstly, to provide an installation structure for a cross-flow fan blade, which, on the basis of reducing the turbulence phenomenon and its turbulence noise of the cross-flow fan blade, improves the air outlet quality of the impeller and / or the formation quality of its internal circulating vortex, thereby effectively ensuring the air volume, efficiency and noise control of the cross-flow fan blade.

[0005] To solve the aforementioned first technical problem, this invention proposes an installation structure for a cross-flow fan blade, comprising a volute and a back plate respectively disposed on the front and back sides of an impeller within an indoor unit. The impeller includes an end plate and blades, and the minimum distances between the blades and the back plate and the volute are S3 and S4, respectively.

[0006] The back plate has a first groove on the second back plate portion opposite to the end plate, and the minimum distance between the first groove and the end plate is S3;

[0007] And / or the volute tongue is provided with a second groove on the second volute tongue portion of the end plate, and the minimum distance between the second groove and the end plate is S4.

[0008] The cross-flow fan blade installation structure described in this invention reduces turbulence and its noise, while improving the airflow quality of the impeller and / or the formation quality of its internal circulating vortex, thus effectively ensuring the airflow, efficiency, and noise control of the cross-flow fan blade.

[0009] Preferably, the back plate is a vortex-shaped structure that further includes a first back plate portion and a third back plate portion. The first back plate portion is opposite to the blade and is arranged alternately with the second back plate portion. The third back plate portion extends downward in a vortex shape along the side near the indoor unit outlet portion. The first groove has a concave cross section and smoothly transitions with the third back plate portion.

[0010] It can fully satisfy the appropriate deceleration of fluid B between the end plate and the back plate at the second back plate section, and also ensure that it can smoothly merge with the main fluid from the first back plate section at the third back plate section.

[0011] Preferably, the third back plate portion includes:

[0012] The third main board section extends from the first back plate section;

[0013] The third auxiliary plate extends from the second back plate.

[0014] The third auxiliary plate portion is convex inward compared to the third main plate portion, and the convex height H1 is gradually increased along the extension direction of the third back plate portion.

[0015] It can reduce the expansion rate of the diffuser section of fluid B when it merges, thereby avoiding the rapid deceleration of fluid B, minimizing turbulence, and suppressing the deterioration of static pressure recovery efficiency of the diffuser section of the indoor unit's air outlet.

[0016] Preferably, the maximum protrusion width of the third auxiliary plate is K4, then K4 / K1 = 1 to 1.5, where K1 is the width of the first groove.

[0017] It can fully cover the flow range of fluid B during the merging process, and also ensure that it can merge smoothly with the main fluid from the third main board.

[0018] Preferably, the volute tongue further includes a first volute tongue portion and a third volute tongue portion, the first volute tongue portion being opposite to the blade and arranged alternately with the second volute tongue portion, the third volute tongue portion extending along the side near the indoor unit outlet portion, and the second groove having a concave cross section and smoothly transitioning with the third volute tongue portion.

[0019] It can both fully satisfy the appropriate deceleration of the fluid C between the end plate and the volute tongue at the second volute tongue and ensure that it can smoothly merge with the main fluid from the first volute tongue at the third volute tongue.

[0020] Preferably, the third cochlear tongue comprises:

[0021] The third main tongue extends from the first cochlear tongue;

[0022] The third accessory lingual part extends from the second cochlear part;

[0023] The third auxiliary tongue portion is convex inward compared to the third main tongue portion, and the convex height H2 is gradually increased along the extension direction of the third cochlear tongue portion.

[0024] This can reduce the expansion rate of the diffuser section of fluid C during confluence, thereby avoiding rapid deceleration of fluid C, minimizing turbulence, and preventing the aerodynamic performance of the indoor unit's airflow from deteriorating.

[0025] Preferably, the maximum height difference of H2 is △H2, then △H2 / H4 = 1 to 2, where H4 is the depth of the second trench.

[0026] When △H2 / H4=1~2, the convex shape of the third volute tongue has a better effect.

[0027] 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, then K1 / K3 = 1.5 to 3 and / or K2 / K3 = 1.5 to 3.

[0028] Taking K1 / K3 = 1.5 to 3 as an example, it can fully cover the flow range of fluid B, and hardly interfere with the main fluid from the first back plate. Similarly, when K2 / K3 = 1.5 to 3, it can fully cover the flow range of fluid C, and hardly interfere with the main fluid from the first volute tongue.

[0029] The technical problem to be solved by the present invention is that: in the second aspect, a wall-mounted indoor unit is provided, and / or in the third aspect, an air conditioner is provided, which, on the basis of reducing the turbulence phenomenon and its turbulence noise of the cross-flow fan blades, improves the air outlet quality of the impeller and / or the formation quality of its internal circulating vortex, and effectively ensures the air volume, efficiency and noise control of the cross-flow fan blades.

[0030] To solve the aforementioned second technical problem, the present invention provides a wall-mounted indoor unit having the installation structure of the cross-flow fan blades described in any embodiment of the first aspect.

[0031] To solve the aforementioned third technical problem, the present invention provides an air conditioner having the mounting structure of the cross-flow fan blades described in any embodiment of the first aspect.

[0032] Compared with the prior art, the cross-flow fan blade installation structure, wall-mounted indoor unit, and air conditioner described in this invention have the following beneficial effects:

[0033] 1) On the basis of reducing the turbulence phenomenon and its turbulence noise of the cross-flow fan blades, improve the air outlet quality of the impeller and / or the formation quality of its internal circulating vortex, so as to effectively ensure the air volume, efficiency and noise control of the cross-flow fan blades.

[0034] 2) It can reduce the expansion rate of the diffuser section when the fluid between the end plate and the back plate merges, thereby avoiding the rapid deceleration of the fluid, minimizing the occurrence of turbulence, and suppressing the deterioration of the static pressure recovery efficiency of the diffuser section of the indoor unit's air outlet.

[0035] 3) It can reduce the expansion rate of the diffuser section when the fluid between the end plate and the volute tongue merges, thereby avoiding rapid deceleration of the fluid, minimizing turbulence, and preventing the aerodynamic performance of the indoor unit's airflow from deteriorating. Attached Figure Description

[0036] The accompanying drawings, which constitute a part of this invention, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0037] Figure 1 This is a schematic diagram of the installation structure of a wall-mounted indoor unit as described in the background section of this invention;

[0038] Figure 2 This is a three-dimensional structural diagram of an impeller according to the present invention;

[0039] Figure 3 This is a three-dimensional structural diagram of a wind turbine blade according to the present invention;

[0040] Figure 4 for Figure 1 A partially enlarged structural diagram;

[0041] Figure 5 This is a schematic diagram of the first installation structure of a back panel in a wall-mounted indoor unit as described in Embodiment 1 of the present invention;

[0042] Figure 6 This is a schematic diagram of the second installation structure of the back panel in the wall-mounted indoor unit as described in Embodiment 1 of the present invention;

[0043] Figure 7 This is a schematic diagram of the first installation structure of a volute tongue in a wall-mounted indoor unit as described in Embodiment 1 of the present invention;

[0044] Figure 8 This is a schematic diagram of the second installation structure of the volute tongue in the wall-mounted indoor unit as described in Embodiment 1 of the present invention;

[0045] Figure 9 This is a plan view of a cross-flow fan blade installation structure as described in Embodiment 1 of the present invention;

[0046] Figure 10 This is a schematic diagram of another type of back panel in the wall-mounted indoor unit as described in Embodiment 2 of the present invention;

[0047] Figure 11 This is a schematic diagram of another type of volute tongue in a wall-mounted indoor unit as described in Embodiment 2 of the present invention;

[0048] Figure 12 This is a plan view of another cross-flow fan blade installation structure described in Embodiment 2 of the present invention.

[0049] Explanation of reference numerals in the attached figures:

[0050] 1-Indoor unit, 2-Heat exchanger, 3-Impeller, 4-Back plate, 401-First back plate section, 402-Second back plate section, 403-Third back plate section, 4031-Third main plate section, 4032-Third auxiliary plate section, 5-Vortex tongue, 501-First vortex tongue section, 502-Second vortex tongue section, 503-Third vortex tongue section, 5031-Third main tongue section, 5032-Third auxiliary tongue section, 6-Air guide plate, 7-Panel, 8-End plate, 9-Blade, 10-Fan blade body, 11-First groove, 12-Second groove, 13-Circulation vortex. Detailed Implementation

[0051] To make the above-mentioned objectives, technical solutions, and advantages of the present invention clearer and more understandable, the present invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only some embodiments constituting the present invention, and are only used to explain the present invention and do not constitute a limitation thereof. Unless otherwise specified, the embodiments and features in the embodiments of the present invention can be combined with each other.

[0052] Example 1

[0053] See Figure 1-9 As shown, the present invention provides an installation structure for a cross-flow fan blade, including a volute 5 and a back plate 4 respectively disposed on the front and back sides of an impeller 3 in an indoor unit 1. The impeller 3 includes an end plate 8 and blades 9. The minimum distances between the blades 9 and the back plate 4 and the volute 5 are S3 and S4 respectively.

[0054] The back plate 4 has a first groove 11 opposite to the second back plate portion 402 of the end plate 8, and the minimum distance between the first groove 11 and the end plate 8 is S3.

[0055] 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.

[0056] Specifically, as described in the background section, the outer diameter D0 of the end plate 8 is larger than the outer diameter D2 of the blade 9. This is because the fan blades 10 are generally injection molded, and the fan blades 10 are then ultrasonically welded together to form the impeller 3. To ensure the resin flow stability of the fan blades 10 during injection molding, as well as the assembly accuracy and allowance during ultrasonic welding, and to prevent the blades 9 from breaking upon drop, D0 must be greater than D2. During ultrasonic welding, multiple fan blades 10 are staggered at a certain angle around the axis of rotation of the impeller 3, so that the axial pressure variation of the impeller 3 maintains a certain phase. Of course, during the injection molding of the fan blades 10, multiple blades 9 are also arranged at unequal intervals, which can significantly improve the noise problem of the cross-flow fan, especially the rotational noise caused by the pressure variation of the rotating blades 9.

[0057] However, considering the assembly precision of impeller 3, the minimum distance between impeller 3 and back plate 4 is actually only the minimum distance between end plate 8 and back plate 4, denoted here as S1, which is smaller than the minimum distance S3 between blade 9 and back plate 4. Similarly, the minimum distance between impeller 3 and volute tongue 5 is actually only the minimum distance between end plate 8 and volute tongue 5, denoted here as S2, which is smaller than the minimum distance S4 between blade 9 and volute tongue 5. Therefore, in the prior art, the airflow direction of impeller 3 and the stability of circulating vortex 13 usually do not reach the ideal state. The reason for this is that D0 > D2: the minimum distance between blade 9 and back plate 4 and / or volute tongue 5 usually does not reach the optimal theoretical distance, but is too large.

[0058] In this 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 groove 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 blade 9 and the back plate 4 (i.e., the first back plate portion 401). Furthermore, firstly, even if the airflow of impeller 3 is forced to split into two streams due to D0 > D2, the fluid B between end plate 8 and back plate 4 will be appropriately slowed down when flowing through the first groove 11, thus allowing fluid B to smoothly merge with the main fluid from between blade 9 and back plate 4. This ensures that the two fluid streams will not interfere with each other and cause turbulence, thereby effectively reducing the turbulence phenomenon and turbulence noise of the cross-flow fan blades. Secondly, when impeller 3 is assembled in the indoor unit 1, the minimum distance S1 between end plate 8 and back plate 4 (i.e., the second back plate part 402) is used as the control benchmark, which can effectively ensure that the minimum distance S3 between blade 9 and back plate 4 is also the optimal theoretical distance S1. Thus, under the action of the vortex structure of back plate 4, it is ensured that the airflow outlet direction of impeller 3 can effectively meet the induction of the static pressure recovery direction.

[0059] 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) will be consistent with the minimum distance S4 between the blade 9 and the volute tongue 5 (i.e., the first volute tongue portion 501). Furthermore, firstly, even if the airflow of impeller 3 is forced to split into two streams due to D0 > D2, the fluid C between end plate 8 and volute tongue 5 will be appropriately slowed down when flowing through the second groove 12, thus allowing fluid C to smoothly merge with the main fluid from between blade 9 and volute tongue 5. This ensures that the two fluid streams will not interfere with each other and cause turbulence, thereby effectively reducing the turbulence phenomenon and turbulence noise of the cross-flow fan blades. Secondly, when impeller 3 is assembled in the indoor unit 1, the minimum distance S2 between end plate 8 and volute tongue 5 (i.e., the second volute tongue 502) is used as the control benchmark, which can effectively ensure that the minimum distance S4 between blade 9 and volute tongue 5 is also the optimal theoretical distance S2, thereby ensuring that the circulating vortex 13 formed in impeller 3 is stable and conforms to the ideal state.

[0060] In summary, the cross-flow fan blade installation structure described in this invention reduces turbulence and its noise, while improving the airflow quality of the impeller and / or the formation quality of its internal circulating vortex, thus effectively ensuring the airflow, efficiency, and noise control of the cross-flow fan blade.

[0061] Preferably, the back plate 4 is a vortex-shaped structure that further includes a first back plate portion 401 and a third back plate portion 403. The first back plate portion 401 is directly opposite the blade 9 and is arranged alternately with the second back plate portion 402. The third back plate portion 403 extends downward in a vortex shape along the side near the outlet of the internal unit 1. The first groove 11 has a concave cross section and smoothly transitions with the third back plate portion 403.

[0062] Specifically, fluid B slows down appropriately when flowing through the first groove 11, and then continues to flow through the third back plate section 403 to merge with the main fluid from the blade 9 and the first back plate section 401. The first groove 11 has a concave cross-section and smoothly transitions to the third back plate section 403, which not only satisfies the appropriate deceleration of fluid B at the second back plate section 402, but also ensures that it can smoothly merge with the main fluid from the first back plate section 401 at the third back plate section 403. Subsequently, the merged airflow can be guided into the room by the air guide plate 6, which is located at the outlet of the indoor unit 1, that is, on the air outlet side below the impeller 3.

[0063] Preferably, the volute tongue 5 further includes a first volute tongue portion 501 and a third volute tongue portion 503. The first volute tongue portion 501 is directly opposite the blade 9 and is arranged alternately with the second volute tongue portion 502. The third volute tongue portion 503 extends along the side near the outlet of the internal unit 1. The second groove 12 has a concave cross section and smoothly transitions with the third volute tongue portion 503.

[0064] Specifically, a panel 7 is installed directly in front of the heat exchanger 2, and the volute tongue 5 is located below and behind the panel 7. The fluid C slows down appropriately as it flows through the second groove 12, and then continues to flow through the third volute tongue 503 to merge with the main fluid from the blade 9 and the first volute tongue 501. The second groove 12 has a concave cross-section and smoothly transitions to the third volute tongue 503, which satisfies the appropriate slowing down of fluid C at the second volute tongue 502 and ensures smooth merging with the main fluid from the first volute tongue 501 at the third volute tongue 503. Subsequently, the merged airflow is guided into the room by the air guide plate 6.

[0065] 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, then K1 / K3 = 1.5~3 and / or K2 / K3 = 1.5~3.

[0066] Specifically, K1 and K2 can be equal or unequal, depending on the requirements. Taking K1 / K3 = 1.5 to 3 as an example, it can fully cover the flow range of fluid B without interfering with the main fluid from the first back plate 401. Similarly, when K2 / K3 = 1.5 to 3, it can fully cover the flow range of fluid C without interfering with the main fluid from the first volute tongue 501.

[0067] Example 2

[0068] Preferably, see Figure 10-12 As shown, the third backplate portion 403 includes:

[0069] The third motherboard portion 4031 extends from the first backplate portion 401;

[0070] The third auxiliary plate portion 4032 extends from the second back plate portion 402;

[0071] The third auxiliary plate portion 4032 is convex inward compared to the third main plate portion 4031, and the convex height H1 is gradually increased along the extending direction of the third back plate portion 403.

[0072] Specifically, since there are no blades 9 near the end plate 8, the radial flow that is not in the same direction as the airflow outlet of the outer periphery of the blades 9 is reduced, meaning that the airflow of the third auxiliary plate section 4032 is smaller than that of the third main plate section 4031. As described in Embodiment 1, fluid B first decelerates at the first groove 11, and then flows through the third auxiliary plate section 4032 at the third back plate section 403 with a small airflow to merge with the large airflow from the third main plate section 4031. At this time, the protrusion at the third auxiliary plate section 4032 reduces the expansion rate of the diffuser section of fluid B when merging, thereby avoiding a rapid deceleration of fluid B, minimizing turbulence, and suppressing the deterioration of the static pressure recovery efficiency of the diffuser section at the air outlet of the indoor unit 1.

[0073] Preferably, the third cochlear tongue 503 includes:

[0074] The third main tongue portion 5031 extends from the first cochlear tongue portion 501;

[0075] The third auxiliary tongue portion 5032 extends from the second cochlear tongue portion 502;

[0076] The third auxiliary tongue portion 5032 is convex inward compared to the third main tongue portion 5031, and the convex height H2 is gradually enlarged along the extension direction of the third worm tongue portion 503.

[0077] Specifically, since there are no blades 9 near the end plate 8, the radial flow that is not in the same direction as the airflow outlet of the outer periphery of the blades 9 is reduced, meaning that the airflow of the third auxiliary tongue 5032 is smaller than that of the third main tongue 5031. As described in Embodiment 1, the fluid C first decelerates at the second groove 12, and then flows through the third auxiliary tongue 5032 at the third volute tongue 503 with a small airflow to merge with the large airflow from the third main tongue 5031. At this time, the protrusion at the third auxiliary tongue 5032 reduces the expansion rate of the diffuser section of the fluid C during merging, thereby avoiding a rapid deceleration of the fluid C, minimizing turbulence, and preventing the aerodynamic performance of the airflow from the indoor unit 1 from deteriorating.

[0078] Preferably, the maximum protrusion width of the third auxiliary plate portion 4032 is K4, and the maximum protrusion width of the third auxiliary tongue portion 5032 is K5, then K4 / K1 = 1~1.5 and / or K5 / K2 = 1~1.5.

[0079] Specifically, the protrusion width of the third auxiliary plate 4032 can be a fixed value, set to be the same width as K1, or a variable value, set to be unequal width to K1, depending on the needs. Taking 1 < K4 / K1 ≤ 1.5 as an example, the protrusion width of the third auxiliary plate 4032 can also be gradually increased along the extension direction of the third back plate 403. In this case, its maximum protrusion width K4 corresponds to the extension end of the third auxiliary plate 4032. Thus, it can fully cover the flow range of fluid B during the merging process, and also ensure that it can merge smoothly with the main fluid from the third main plate 4031.

[0080] Similarly, the protrusion width of the third auxiliary tongue 5032 can be a fixed value set to be the same width as K2, or a variable value set to be unequal in width to K2, depending on the needs. Taking 1 < K5 / K2 ≤ 1.5 as an example, the protrusion width of the third auxiliary tongue 5032 can also be gradually increased along the extension direction of the third volute tongue 503. In this case, its maximum protrusion width K5 corresponds to the extension end of the third auxiliary tongue 5032. Thus, it can fully cover the flow range of fluid C during the merging process, and also ensure that it can merge smoothly with the main fluid from the third main tongue 5031.

[0081] Preferably, the maximum height difference of H1 is ΔH1, and the maximum height difference of H2 is ΔH2, then:

[0082] The depth of the first groove 11 is H3, and ΔH1 / H3 = 1 to 2;

[0083] And / or the groove depth of the second groove 12 is H4, ΔH2 / H4 = 1~2.

[0084] Specifically, the extension length of the third back plate 403 is actually much greater than the length of the second back plate 402. This means that the flow range of fluid B during the merging process is greater than the flow range when it flows through the first groove 11. Consequently, when ΔH1 / H3 = 1 to 2, the convex shape of the third auxiliary plate 4032 has a better effect.

[0085] Similarly, the extension length of the third volute tongue 503 is actually much greater than the length of the second volute tongue 502. The corresponding flow range of fluid C during the merging process will be greater than the flow range when it flows through the second groove 12. Therefore, when ΔH2 / H4=1~2, the convex setting effect of the third volute tongue 5032 is better.

[0086] Example 3

[0087] The present invention also provides a wall-mounted indoor unit having the installation structure of the cross-flow fan blades described in any of the embodiments 1-2.

[0088] The present invention also provides an air conditioner having an installation structure for the cross-flow fan blades as described in any of the embodiments 1-2.

[0089] Specifically, those skilled in the art will understand that when the wall-mounted indoor unit and / or air conditioner provided in Embodiment 3 have the cross-flow fan blade installation structure described in any of Embodiments 1-2, the solution to the corresponding technical problem and the achievement of the technical effect can be found in the description of the cross-flow fan blade installation structure in Embodiments 1-2, and will not be repeated here.

[0090] While the present invention has been disclosed above, it is not limited thereto. Any person skilled in the art can make various modifications and alterations without departing from the spirit and scope of the invention; therefore, the scope of protection of the present invention should be determined by the scope defined in the claims.

Claims

1. An installation structure for a cross-flow fan blade, characterized in that, The impeller (3) includes a volute tongue (5) and a back plate (4) located on the front and back sides of the impeller (3) in the inner unit (1). The impeller (3) includes an end plate (8) and blades (9). The minimum distances between the blades (9) and the back plate (4) and the volute tongue (5) are S3 and S4, respectively. Then: The back plate (4) has a first groove (11) on the second back plate portion (402) opposite to 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) on 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; The back plate (4) is a vortex structure that also includes a first back plate part (401) and a third back plate part (403). The third back plate part (403) extends downward in a vortex shape along the side near the outlet of the internal unit (1). The first groove (11) has a concave cross section and smoothly transitions with the third back plate part (403). The third back plate portion (403) includes: The third main board section (4031) extends from the first back plate section (401). The third auxiliary plate (4032) extends from the second back plate (402). The third auxiliary plate portion (4032) is convex inward compared to the third main plate portion (4031), and the convex height H1 is gradually increased along the extension direction of the third back plate portion (403). The indoor unit (1) is equipped with a heat exchanger (2), and a panel (7) is installed in front of the heat exchanger (2). The volute tongue (5) is located at the lower rear of the panel (7).

2. The installation structure of a cross-flow fan blade according to claim 1, characterized in that, The first back plate portion (401) is positioned opposite the blade (9) and is arranged in an alternating manner with the second back plate portion (402).

3. The installation structure of a cross-flow fan blade according to claim 1, characterized in that, The maximum protrusion width of the third auxiliary plate (4032) is K4, then K4 / K1 = 1~1.5, where K1 is the width of the first groove (11).

4. The installation structure of a cross-flow fan blade according to claim 1, characterized in that, The volute tongue (5) further includes a first volute tongue portion (501) and a third volute tongue portion (503). The first volute tongue portion (501) is opposite to the blade (9) and is arranged alternately with the second volute tongue portion (502). The third volute tongue portion (503) extends along the side near the outlet of the internal unit (1). The second groove (12) has a concave cross section and smoothly transitions with the third volute tongue portion (503).

5. The installation structure of a cross-flow fan blade according to claim 4, characterized in that, The third cochlear tongue (503) includes: The third main tongue portion (5031) extends from the first cochlear tongue portion (501). The third accessory lingual part (5032) extends from the second cochlear part (502); The third auxiliary tongue portion (5032) is convex inward compared to the third main tongue portion (5031), and the convex height H2 is gradually enlarged along the extension direction of the third worm tongue portion (503).

6. The installation structure of a cross-flow fan blade according to claim 5, characterized in that, The maximum height difference of H2 is △H2, then △H2 / H4 = 1~2, where H4 is the depth of the second trench (12).

7. The mounting structure of a cross-flow fan blade according to any one of claims 1-6, characterized in that, 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, then K1 / K3 = 1.5~3 and / or K2 / K3 = 1.5~3.

8. A wall-mounted indoor unit, characterized in that, The wall-mounted indoor unit has the mounting structure of the cross-flow fan blades as described in any one of claims 1-7.

9. An air conditioner, characterized in that, The air conditioner has the mounting structure of the cross-flow fan blades as described in any one of claims 1-7.

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