Backflow suppression device and backflow prevention fan, refrigerator containing the backflow suppression device

Abstract

This invention discloses a backflow suppression device and an anti-backflow fan and refrigerator including the same. The backflow suppression device is used to suppress the backflow of gas from the air inlet of the fan to the outside of the fan. It includes: a flow-suppressing part, which is arranged around the outer edge of the air inlet, with one side of the flow-suppressing part rotatably connected to the outer edge of the air inlet, and the other side of the flow-suppressing part extending towards the axis of the air inlet, and the flow-suppressing part being used to rotate around the outer edge of the air inlet; and a limiting part, which is arranged around the outer edge of the air inlet, and the limiting part being used to restrict the rotation of the flow-suppressing part towards the outside of the fan. When gas backflows from the air inlet, the flow-suppressing part rotates towards the limiting part; when air enters the air inlet, the flow-suppressing part rotates towards the impeller of the fan. The flow-suppressing part can block the backflow generated in the positive pressure zone, thereby reducing eddies and the noise generated by eddies. It reduces repetitive work, thereby improving the efficiency of the fan and reducing energy consumption.

Description

Technical Field

[0001] The present invention relates in particular to a backflow suppression device and a backflow prevention fan and refrigerator containing the same. Background Technology

[0002] As consumers increasingly demand larger capacity, multiple temperature zones, precise temperature control, energy efficiency, and quiet operation from refrigerators, the design of the air duct system in frost-free refrigerators has become increasingly complex and crucial. Modern high-end refrigerators generally adopt a multi-temperature zone design, such as a refrigerator compartment and a variable temperature compartment, each requiring independent cooling supply and precise temperature control. To achieve this, the air duct system typically starts from a single evaporator and fan, designing multiple branch channels, and distributing cold air as needed through the opening and closing of electrically controlled dampers.

[0003] In existing air duct systems, the fan outlet branches into two branches, left and right, leading to different temperature zones or different locations within the same temperature zone. In actual operation, the controller selectively opens the damper on one side and closes the other, based on the temperature requirements of each zone under different operating modes. This "single-sided damper operation" mode is the standard operating state for refrigerators to achieve precise and differentiated airflow.

[0004] In practical use, it was found that when the system is in single-sided damper operation mode, the pressure distribution at the fan intake exhibits significant asymmetry. The intake area near the open-side damper is a normal negative pressure zone, while the edge area of ​​the intake corresponding to the closed-side damper is no longer negative pressure, but rather a positive pressure zone appears. The formation of the positive pressure zone is due to the increase in static pressure at the closed-side damper. The presence of the positive pressure zone causes gas to "leak" back to the fan intake side through the gap between the fan impeller and the casing, thus forming a recirculation zone at the edge of the intake far from the open-side damper. The airflow velocity vector direction in the recirculation zone is opposite to the intake direction of the fan, and is often accompanied by vortices. This reduces fan efficiency, increases energy consumption, increases fan noise, and also leads to poor airflow uniformity to the evaporator downstream of the fan, causing localized frost formation in the room. Summary of the Invention

[0005] The technical problem to be solved by the present invention is to overcome the defects in the prior art where, when one side of the damper is open and the other side is closed, the air inlet of the fan is away from the edge of the open side damper, forming a positive pressure zone, which causes gas backflow, resulting in reduced fan efficiency, increased energy consumption, and increased fan noise. The present invention provides a backflow suppression device and an anti-backflow fan and refrigerator including the device.

[0006] The present invention solves the above-mentioned technical problems through the following technical solution:

[0007] A backflow suppression device is used to suppress the backflow of gas from the air inlet of a fan to outside the fan. The backflow suppression device includes:

[0008] A flow-suppressing part is provided around the outer edge of the air inlet. One side of the flow-suppressing part is rotatably connected to the outer edge of the air inlet, and the other side of the flow-suppressing part extends toward the axis of the air inlet. The flow-suppressing part is used to rotate around the outer edge of the air inlet.

[0009] A limiting part is provided around the outer edge of the air inlet. The limiting part is used to restrict the flow suppressing part from rotating outward from the fan. When the gas in the air inlet flows back, the flow suppressing part rotates toward the limiting part. When the air inlet is receiving air, the flow suppressing part rotates toward the impeller of the fan.

[0010] In this design, a flow-damping section is incorporated. When the outer edge of the air inlet rotates, and a positive pressure zone appears at the inlet, the flow-damping section surrounding the inlet can block the backflow generated by the positive pressure zone, preventing gas from flowing back to the outside of the fan. This reduces eddies and the noise generated by eddies. The flow-damping section is driven by the gas inside the fan, eliminating the need for an additional drive structure. It can also adaptively activate in positive pressure zones, resulting in a more timely response and lower cost. Simultaneously, a limiting section restricts the rotation position of the flow-damping section, preventing it from flipping outside the fan. This ensures the suppression of backflow and prevents gas pressurized by the fan from flowing out of the inlet and being re-drawn into the inlet, thus reducing redundant work, improving fan efficiency, and lowering energy consumption. Compared to fans with existing backflow, fans with this backflow suppression device deliver a more sufficient and uniform airflow.

[0011] Preferably, the flow-suppressing part includes a first blade and a second blade, and multiple first blades and second blades are provided. Along the outer circumferential direction of the air inlet, the first blade has a first overlapping edge corresponding to the end of the second blade, and the second blade has a second overlapping edge corresponding to the end of the first blade. The first overlapping edge and the second overlapping edge overlap each other and are staggered along the thickness direction of the first blade or the second blade. The end of the first overlapping edge is spaced apart from the body of the second blade, and the end of the second overlapping edge is spaced apart from the body of the first blade. When air enters the air inlet and gas backflow occurs in a local area of ​​the outer edge of the air inlet, the first blade corresponding to the gas backflow area drives the second blade to rotate toward the limiting part, while the first blade in the remaining area drives the second blade to rotate toward the impeller of the fan.

[0012] When air enters through the air inlet and gas backflow occurs in all areas of the outer edge of the air inlet, all the first blades and the second blades rotate toward the limiting part simultaneously.

[0013] When air enters through the air inlet and there is no gas backflow in any area of ​​the outer edge of the air inlet, all the first blades and the second blades rotate toward the impeller of the fan.

[0014] In this design, the above-mentioned configuration allows the first or second blade to rotate towards the limiting part when air enters the inlet and gas recirculation occurs in a localized area of ​​the inlet, thus blocking the gas recirculation. When air enters the inlet and gas recirculation occurs in all areas of the inlet, both the first and second blades can rotate to block the gas recirculation at the inlet. When air enters the inlet and there is no gas recirculation, both the first and second blades can rotate towards the impeller to ensure sufficient air intake. The first and second overlapping edges are used to drive the adjacent first and second blades to rotate. In areas without gas recirculation, the rotation of the first and second blades is relatively independent; that is, some of the first and second blades can rotate towards the limiting part, while others can rotate towards the impeller. They can rotate in different directions without affecting each other.

[0015] Preferably, the surface of the first overlapping edge used to overlap the second overlapping edge extends from the body of the first blade to the middle area of ​​the first overlapping edge and is provided with an inclined slope or an arc-shaped slope.

[0016] Alternatively, the surface of the second overlapping edge used to overlap the first overlapping edge extends from the body of the second blade to the middle area of ​​the second overlapping edge and is provided with an inclined slope or an arc-shaped slope.

[0017] In this solution, the above-mentioned arrangement reduces the contact area between the first overlapping edge and the second overlapping edge by using an inclined slope or an arc-shaped slope. Compared to the first overlapping edge and the second overlapping edge having a flat surface and a large contact area with a certain wall adhesion effect, when air enters the air inlet and the gas flows back in a local area of ​​the air inlet, it is beneficial for the overlapping parts of the first blade and the second blade to separate from each other, making it easier for some of the first blade and the second blade to rotate individually toward the limiting part.

[0018] Preferably, the first blade and the second blade extend for the same length from the outer edge of the air inlet toward the axis of the air inlet, and when air enters through the air inlet, the angle between the first blade and the second blade and the limiting portion is α, wherein 10°≤α≤80°.

[0019] In this solution, the above-mentioned settings are used to limit the flow suppression part from turning outward from the fan by the limiting part, and the air intake efficiency and backflow suppression performance of the fan are ensured by limiting the turning angle.

[0020] Preferably, when air enters through the air inlet and no gas backflow occurs in any area of ​​the outer edge of the air inlet, the distance between the first blade and the second blade on the outer edge away from the air inlet and the impeller of the fan along the axial direction of the fan is W1, where W1 = H - Lsinα ≥ 5 mm.

[0021] When air enters through the air inlet and no gas backflow occurs in any area of ​​the outer edge of the air inlet, the diameter of the first blade and the second blade on the outer edge away from the air inlet along the radial direction of the fan is W2, where W2 = D2 - 2Lcosα, and the value range of W2 is 0.75D1 ≤ D2 - 2Lcosα ≤ D1 - 5mm. Here, H is the axial distance from the outer edge end of the fan impeller near the air inlet to the outer edge of the first blade and the second blade facing the air inlet, L is the extension length of the flow suppression part from the outer edge near the air inlet to the outer edge away from the air inlet, D1 is the outer edge diameter of the fan impeller, and D2 is the outer edge diameter of the flow suppression part.

[0022] In this solution, the above settings limit the axial position and radial dimension of the flow suppressor on the side away from the outer edge of the air inlet during the air intake state. This prevents the flow suppressor from being too close to the impeller of the fan on the side away from the outer edge of the air inlet, and also prevents the flow suppressor from having too small a diameter on the side away from the outer edge of the air inlet, which would affect the air intake efficiency of the fan.

[0023] Preferably, along the outer circumferential direction of the air inlet, the central angle corresponding to the extension dimension of the first blade is θ1, and the central angle corresponding to the extension dimension of the second blade is θ2, wherein 0 < θ1 < 30°, and 0.5θ1 ≤ θ2 ≤ 1.5θ1.

[0024] In this solution, the above settings are used to avoid a situation where the difference in the central angles corresponding to the extension dimensions of the first and second blades is too large, resulting in the maximum turning angle of the flow suppressor into the fan being too small, thus affecting the fan's air intake efficiency.

[0025] Preferably, the first blade has a first protrusion in the middle region of the side facing the outer edge of the air inlet, and the second blade has a second protrusion in the middle region of the side facing the outer edge of the air inlet. The outer edge of the air inlet has a groove and a rotating shaft corresponding to the first and second protrusions. The rotating shaft extends from the inner wall of the groove and passes through the first and second protrusions. Along the circumferential direction of the outer edge of the air inlet, the extension dimension of the first protrusion corresponds to a central angle β1, and the extension dimension of the second protrusion corresponds to a central angle β2, wherein 0.2θ1≤β1≤0.8θ1, 0.2θ2≤β2≤0.8θ2.

[0026] In this solution, the above settings limit the range of the central angle corresponding to the extension dimensions of the first and second protrusions to ensure that the first and second protrusions can drive the first and second blades to rotate freely, thus avoiding the situation where the first and second blades fall off after multiple rotations due to insufficient load-bearing capacity caused by the excessively small extension dimensions of the first and second protrusions.

[0027] Preferably, the extension dimension of the first protrusion or the second protrusion into the groove is L1, wherein 0.1L≤L1≤L2≤0.5L, L2 is the extension length of the limiting part from the outer edge of the air inlet toward the axis of the air inlet, and L is the extension length of the flow suppressing part from the outer edge near the air inlet.

[0028] In this solution, the load-bearing capacity of the first or second protrusion is further guaranteed by limiting the extension dimension of the first or second protrusion into the groove.

[0029] A backflow prevention fan, the backflow prevention fan including the backflow suppression device as described above.

[0030] In this solution, the anti-backflow fan includes the aforementioned backflow suppression device. The backflow is reduced when the air inlet is under local positive pressure by the cooperation of the flow suppression part and the limiting part. There is no need to set up an additional detection mechanism and drive mechanism. The rotation of the flow suppression part follows the gas flow state, which reduces costs and provides a more timely response. It reduces repetitive work, thereby improving the efficiency of the fan and reducing energy consumption.

[0031] A refrigerator comprising an anti-backflow fan as described above.

[0032] In this solution, the refrigerator includes the aforementioned anti-backflow fan to utilize the anti-backflow fan's ability to suppress gas backflow, reduce backflow eddies, and lower the fan's own noise. At the same time, the refrigerator with the anti-backflow fan provides more sufficient and more uniform airflow to each compartment, avoiding localized frost formation caused by uneven airflow on the evaporator surface of the refrigerator.

[0033] The significant advantages of this invention are as follows: By incorporating a flow-suppressing section, when a positive pressure zone appears at the air inlet due to rotation of the outer edge of the inlet, the flow-suppressing section surrounding the inlet can block the backflow generated by the positive pressure zone, preventing gas from flowing back to the outside of the fan, thereby reducing eddies and the noise generated by eddies. The flow-suppressing section is driven by the gas inside the fan, eliminating the need for an additional drive structure, and can adaptively activate in positive pressure zones, resulting in a more timely response and lower cost. Simultaneously, a limiting section restricts the rotation position of the flow-suppressing section, preventing it from flipping outside the fan, thus ensuring the suppression of backflow and preventing gas pressurized by the fan from flowing out of the inlet and being re-drawn into the inlet, reducing redundant work and improving fan efficiency and reducing energy consumption. Compared to fans with existing backflow, fans with this backflow suppression device deliver a more sufficient and uniform airflow. Attached Figure Description

[0034] Figure 1 This is a diagram showing the positional relationship between the air inlet and the impeller in a preferred embodiment of the present invention.

[0035] Figure 2 This is a diagram showing the positional relationship between the flow-suppressing part and the limiting part in a preferred embodiment of the present invention.

[0036] Figure 3 This is a diagram showing the positional relationship between the flow-damping section and the fan impeller in a preferred embodiment of the present invention.

[0037] Figure 4 This is a schematic diagram of the flow suppression section according to a preferred embodiment of the present invention.

[0038] Figure 5 This is a diagram showing the positional relationship between the groove and the limiting part in a preferred embodiment of the present invention.

[0039] Figure 6 This is a schematic diagram of the structure of the first and second blades when air is introduced into the air inlet and gas flows back to the outer edge in a preferred embodiment of the present invention.

[0040] Figure 7 This is a diagram showing the positional relationship between the first overlapping edge and the second overlapping edge according to a preferred embodiment of the present invention.

[0041] Figure 8 This is a schematic diagram of the structure of the first blade and the second blade when the air inlet is intaked and there is no gas backflow at the outer edge, according to a preferred embodiment of the present invention.

[0042] Figure 9 This is a schematic diagram of the structure of the first and second blades when air is introduced into the air inlet and the gas flows back to the outer edge in a preferred embodiment of the present invention.

[0043] Figure 10This is a schematic diagram of the overlapping structure of the first overlapping edge and the second overlapping edge in a preferred embodiment of the present invention.

[0044] Figure 11 This is a schematic diagram of the structure of the first blade and the second blade according to a preferred embodiment of the present invention.

[0045] Explanation of reference numerals in the attached figures:

[0046] Air Inlet 1

[0047] Outer edge 11

[0048] Groove 12

[0049] Shaft 13

[0050] Flow suppression part 2

[0051] First leaf 21

[0052] First protrusion 211

[0053] Second blade 22

[0054] Second protrusion 221

[0055] First overlapping edge 23

[0056] Second lap edge 24

[0057] 25° sloping surface

[0058] Limiting part 3

[0059] Fan 100

[0060] Impeller 101 Detailed Implementation

[0061] The present invention will be further illustrated by way of embodiments below, but the present invention is not limited to the scope of the embodiments described herein.

[0062] This embodiment provides a backflow suppression device, the specific structure of which is as follows: Figure 1 , Figure 2 , Figure 3 , Figure 4 , Figure 5 , Figure 6 , Figure 7 and Figure 8 As shown, the backflow suppression device is used to suppress the backflow of gas from the air inlet 1 of the fan 100 to outside the fan 100. The backflow suppression device includes:

[0063] The flow-suppressing part 2 is arranged around the outer edge 11 of the air inlet 1. One side of the flow-suppressing part 2 is rotatably connected to the outer edge 11 of the air inlet 1, and the other side of the flow-suppressing part 2 extends toward the axis of the air inlet 1. The flow-suppressing part 2 is used to rotate around the outer edge 11 of the air inlet 1.

[0064] The limiting part 3 is arranged around the outer edge 11 of the air inlet 1. The limiting part 3 is used to restrict the flow suppressing part 2 from rotating outward from the fan 100. When the gas in the air inlet 1 flows back, the flow suppressing part 2 rotates toward the limiting part 3. When the air inlet 1 receives air, the flow suppressing part 2 rotates toward the impeller 101 of the fan 100.

[0065] Specifically, the outer edge 11 of the air inlet 1 is an annular edge. The fan 100 draws in gas through the air inlet 1, which is existing technology and will not be described in detail here. The flow-damping part 2 is an arc-shaped plate, which is arranged around the outer edge 11. One side of the flow-damping part 2 is rotatably connected to the outer edge 11, and the other side extends toward the axis of the air inlet 1. The flow-damping part 2 is rotatably connected to the outer edge 11 and can rotate toward the inside of the fan 100. Specifically, when air is drawn in through the air inlet 1, the flow-damping part 2 rotates toward the inside of the air inlet 1 along with the gas. At this time, the impeller 101 of the fan 100 generates negative pressure, which is used to draw in gas. When some of the multiple air ducts connected to the fan 100 are closed, a positive pressure zone is formed in the corresponding area inside the fan 100 due to the increase in static pressure. This positive pressure zone causes gas inside the fan 100 to flow out from a portion of the outer edge 11 and be drawn back in. At this time, the outer edge 11, equipped with the flow-damping section 2, rotates along with the gas flowing out of the fan 100 and blocks the outward flow of gas due to the presence of the positive pressure zone, thus preventing gas from flowing back to the outside of the fan 100. In other words, the rotation of the flow-damping section 2 is driven by the gas, eliminating the need for an additional drive mechanism. By using the flow-damping section 2 to prevent gas from flowing back to the outside of the fan 100, eddies and the noise generated by eddies are reduced, thereby improving the user experience. The rotation of the flow-damping section 2 can adaptively activate in response to the presence of a positive pressure zone, resulting in a more timely response and lower cost.

[0066] Furthermore, this embodiment also includes a limiting part 3, which is an annular plate extending from the outer edge 11 towards the axis of the air inlet 1. The limiting part 3 and the outer edge 11 are located on the same plane. The limiting part 3 is used to limit the angle of rotation of the flow-suppressing part 2 from inside the fan 100 to the outside. That is, by limiting the rotation position of the flow-suppressing part 2, the limiting part 3 is used to prevent the flow-suppressing part 2 from flipping outside the fan 100, and to prevent the flow-suppressing part 2 from tilting from inside to outside the fan 100, so that the gas backflow can flow out of the fan 100 through the flow-suppressing part 2. This ensures the suppression effect on gas backflow, and prevents the gas that has been pressurized by the fan 100 from flowing out of the air inlet 1 and then being re-intaken into the air inlet 1 by the fan 100, thereby reducing repeated work, improving the efficiency of the fan 100 and reducing energy consumption. Meanwhile, it is understandable that, compared with a fan that has backflow and does not have a backflow suppression structure, the fan 100 with the backflow suppression device has a more sufficient air volume and a more uniform air supply, which restricts the backflow of gas in the positive pressure zone by using the backflow suppression part 2.

[0067] Furthermore, in this embodiment, the flow suppression part 2 includes a first blade 21 and a second blade 22. Multiple first blades 21 and second blades 22 are provided. Along the circumferential direction of the outer edge 11 of the air inlet 1, the first blade 21 is provided with a first overlapping edge 23 corresponding to the end of the second blade 22, and the second blade 22 is provided with a second overlapping edge 24 corresponding to the end of the first blade 21. The first overlapping edge 23 and the second overlapping edge 24 overlap each other and are staggered along the thickness direction of the first blade 21 or the second blade 22. The end of the first overlapping edge 23 is spaced apart from the main body of the second blade 22, and the end of the second overlapping edge 24 is spaced apart from the main body of the first blade 21. When air enters the air inlet 1 and gas backflow occurs in a local area of ​​the outer edge 11 of the air inlet 1, the first blade 21 corresponding to the gas backflow area drives the second blade 22 to rotate toward the limiting part 3, while the first blade 21 in the remaining area drives the second blade 22 to rotate toward the impeller 101 of the fan 100.

[0068] When air enters through the air inlet 1 and gas backflow occurs in all areas of the outer edge 11 of the air inlet 1, all the first blades 21 and the second blades 22 rotate toward the limiting part 3 at the same time.

[0069] When air enters through the air inlet 1 and no gas backflow occurs in any area of ​​the outer edge 11 of the air inlet 1, all the first blades 21 and the second blades 22 rotate toward the impeller 101 of the fan 100.

[0070] Specifically, the first blade 21 and the second blade 22 are arc-shaped plates with a "T"-shaped cross-section. The two ends of the "T"-shaped structure are the first overlapping edge 23 of the first blade 21 and the second overlapping edge 24 of the second blade 22. The main body of the first blade 21 and the second blade 22 is the middle region of the "T"-shaped structure. The first overlapping edge 23 and the second overlapping edge 24 are alternately arranged along the thickness direction of the first blade 21 and the second blade 22. The end of the first overlapping edge 23 is spaced apart from the main body of the second blade 22, and the end of the second overlapping edge 24... The ends of the blades 21 and 22 are spaced apart from each other. When air enters through the inlet 1, the blades 21 and 22 rotate toward the impeller 101. Because the first overlapping edge 23 and the second overlapping edge 24 are spaced apart from the bodies of the blades 21 and 22, respectively, the first overlapping edge 23 and the second overlapping edge 24 overlap each other and partially overlap along the thickness direction of the blades 21 and 22, rather than completely overlapping. This ensures that the first overlapping edge 23 and the second overlapping edge 24 do not restrict the rotation of the blades 21 and 22 toward the impeller 101. Similarly, the first overlapping edge 23 and the second overlapping edge 24 also allow the blades 21 and 22 to rotate toward the limiting part 3 when the gas flows back, without restricting their rotation due to the first overlapping edge 23 and the second overlapping edge 24 directly abutting against the bodies of the blades 21 and 22.

[0071] In this embodiment, there are three situations: when air enters through the air inlet 1 and gas backflow occurs in a local area of ​​the outer edge 11 of the air inlet 1, the first blade 21 corresponding to the gas backflow area drives the second blade 22 to rotate toward the limiting part 3, while the first blade 21 in the remaining area drives the second blade 22 to rotate toward the impeller 101 of the fan 100. Taking the example of the first overlapping edge 23 being located above the second overlapping edge 24, the first blade 21 and the second blade 22 are connected by the first overlapping edge 23 and the second overlapping edge 24, and the first overlapping edge 23 and the second overlapping edge 24 are stacked sequentially along the thickness direction of the first blade 21 and the second blade 22. When the edge of the gas recirculation area corresponds to the first blade 21, the second overlapping edge 24 located below the first overlapping edge 23 and adjacent to the first blade 21 will not be affected by the impact force of the gas recirculation, but will still be affected by the force of the air intake 1 rotating towards the impeller 101. That is, the second blade 22 adjacent to the first blade 21 and close to the edge of the gas recirculation area rotates towards the impeller 101, while the first blade 21 and the second blade 22 located at the edge of the gas recirculation area rotate towards the limiting part 3. From an overall perspective, among the multiple first blades 21 and second blades 22, the first blades 21 and the second blades 22 located in the gas recirculation area rotate towards the limiting part 3, while the remaining area of ​​the first blades 21 drives the second blades 22 to rotate towards the impeller 101 of the fan 100.

[0072] When air enters through the air inlet 1 and gas backflow occurs in all areas of the outer edge 11 of the air inlet 1, all the first blades 21 and second blades 22 rotate simultaneously toward the limiting part 3. It can be understood that when the first blades 21 and second blades 22 rotate toward the limiting part 3, the partially overlapping first overlapping edge 23 and second overlapping edge 24 can also prevent gas backflow to the outside of the fan 100. That is, when air enters through the air inlet 1 and gas backflow occurs in all areas of the outer edge 11 of the air inlet 1, all the first blades 21 and second blades 22 are linked through the first overlapping edge 23 and second overlapping edge 24, and the partially overlapping first overlapping edge 23 and second overlapping edge 24 rotate toward the limiting part 3, forming a complete annular structure with the first blades 21 and second blades 22 to improve the backflow suppression effect.

[0073] When air enters through the air inlet 1 and no gas backflow occurs in any area of ​​the outer edge 11 of the air inlet 1, all the first blades 21 and the second blades 22 rotate toward the impeller 101 of the fan 100. The first blades 21 and the second blades 22 form a complete annular structure that rotates toward the impeller 101 through the partially overlapping first overlapping edge 23 and the second overlapping edge 24, thereby improving the air guiding effect of the air inlet 1 when it enters the air.

[0074] In this embodiment, the surface of the first overlapping edge 23 for overlapping the second overlapping edge 24 extends from the main body of the first blade 21 to the middle area of ​​the first overlapping edge 23 and is provided with an inclined slope 25 or an arc-shaped slope.

[0075] Specifically, the inclined slope 25 or the arc-shaped slope extends in the direction of the surface of the main body of the first blade 21 near the first overlapping edge 23, and is inclined towards the middle area of ​​the first overlapping edge 23 at the junction of the surface of the first blade 21 and the first overlapping edge 23. Compared to the surface of the first overlapping edge 23 used to overlap the second overlapping edge 24 and the surface of the second overlapping edge 24 used to overlap the first overlapping edge 23 being parallel and flat, the inclined slope 25 allows for a more even distribution of the inclined slope 25 near the middle area of ​​the first overlapping edge 23. A sharp corner is formed in the area, which is used to overlap the second overlapping edge 24 to reduce the contact area between the first overlapping edge 23 and the second overlapping edge 24. Compared with the first overlapping edge 23 and the second overlapping edge 24 having a flat surface and a large contact area, and having a certain wall adhesion effect, when air enters through the air inlet 1 and the gas flows back in a local area of ​​the air inlet 1, it is beneficial for the overlapping parts of the first blade 21 and the second blade 22 to separate from each other, making it easier for some of the first blade 21 and the second blade 22 to rotate individually toward the limiting part 3.

[0076] Of course, the inclined slope 25 can also be replaced with an arc-shaped slope, which has the same effect, and will not be elaborated on here.

[0077] Similarly, in other embodiments, the surface of the second overlapping edge 24 that overlaps the first overlapping edge 23 is provided with an inclined slope 25 or an arc-shaped slope extending from the main body of the second blade 22 to the middle area of ​​the second overlapping edge 24. The function is the same, and will not be described in detail here.

[0078] In this embodiment, the first blade 21 and the second blade 22 extend the same length from the outer edge 11 of the air inlet 1 toward the axis of the air inlet 1. When air enters the air inlet 1, the angle between the first blade 21 and the second blade 22 and the limiting part 3 is α, where 10°≤α≤80°.

[0079] Specifically, the first blade 21 and the second blade 22 extend to the same length from the outer edge 11 of the air inlet 1 toward the axis of the air inlet 1, thereby ensuring that the extension size of the flow suppressing part 2 toward the axis of the air inlet 1 is limited, and avoiding the flow suppressing part 2 from extending too much and affecting the air intake efficiency and air intake volume of the fan 100. Furthermore, when air enters through the air inlet 1, the first blade 21 and the second blade 22 rotate simultaneously into the fan 100. By limiting the range of the angle between the first blade 21 and the second blade 22 and the limiting part 3 when air enters through the air inlet 1, compared to when the angle between the first blade 21 and the second blade 22 and the limiting part 3 is 0-90°, it can ensure sufficient air intake while preventing the first blade 21 and the second blade 22 from rotating too much into the fan 100 when air enters through the air inlet 1, for example, when the angle between the first blade 21 and the second blade 22 and the limiting part 3 is 90°, thus preventing the gas from entering the circumferential area of ​​the impeller 101 facing the air inlet 1. This avoids a gas "vacuum" on the circumferential side of the impeller 101 facing the air inlet 1, which would affect the working efficiency of the fan 100.

[0080] Similarly, when the first blade 21 and the second blade 22 form an angle of 0° with the limiting part 3 during the gas recirculation at the air inlet 1, and the air inlet 1 still needs to draw in gas, if the rotation angle of the first blade 21 and the second blade 22 is too large, the diameter of the air inlet 1 used for air intake will be reduced, affecting the air intake volume. In this embodiment, by limiting the rotation angle of the first blade 21 and the second blade 22 and the extension dimension of the first blade 21 and the second blade 22 toward the axis of the air inlet 1, the diameter of the air inlet 1 of the fan 100 used for air intake is guaranteed, thereby ensuring the air intake volume, air intake efficiency and backflow suppression performance of the fan 100.

[0081] In this embodiment, when air enters through the air inlet 1 and no gas backflow occurs in any area of ​​the outer edge 11 of the air inlet 1, the distance between the first blade 21 and the second blade 22 on the side away from the outer edge 11 of the air inlet 1 and the impeller 101 of the fan 100 along the axial direction of the fan 100 is W1, where W1 = H - Lsinα ≥ 5 mm.

[0082] Specifically, W1 is the axial spacing. When the first blade 21 and the second blade 22 rotate toward the inside of the fan 100, the distance between the free side of the first blade 21 and the second blade 22 away from the outer edge 11 of the air inlet 1, that is, the distance between the end of the impeller 101 near the air inlet 1 and the free side of the first blade 21 and the second blade 22 away from the rotating side, is W1. H is the axial distance between the end of the impeller 101 near the outer edge 11 of the fan 100 and the side of the first blade 21 and the second blade 22 facing the outer edge 11 of the air inlet 1. L is the extension length of the flow suppression part 2 from the outer edge 11 near the air inlet 1 to the outer edge 11 away from the air inlet 1. H is determined according to the actual size. When W1 is greater than or equal to 5mm and the value range of α is 10°≤α≤80°, the value range of L is calculated by reverse calculation using trigonometric functions. The calculation of trigonometric functions is existing technology and will not be elaborated on here. This limits the distance L between the outer edge 11 near the air inlet 1 and the opposite sides of the outer edge 11 away from the air inlet 1, thus preventing the flow-suppressing part 2 from extending too far toward the axis of the air inlet 1.

[0083] At the same time, by limiting W1 to be greater than or equal to 5mm, the side of the flow suppression part 2 facing away from the outer edge 11 of the air inlet 1 is prevented from being too close to the end of the impeller 101 near the air inlet 1 in the air intake state, so as to prevent the gas "vacuum" from appearing on the periphery of the end of the impeller 101 facing the air inlet 1, which would affect the working efficiency of the fan 100.

[0084] Similarly, when air enters through the air inlet 1 and no gas backflow occurs in any area of ​​the outer edge 11 of the air inlet 1, the diameter of the first blade 21 and the second blade 22 on the side away from the outer edge 11 of the air inlet 1 along the radial direction of the fan 100 is W2, W2=D2-2Lcosα, and the value range of W2 is 0.75D1≤D2-2Lcosα≤D1-5mm, where D1 is the outer edge diameter of the impeller 101 of the fan 100, and D2 is the outer edge diameter of the flow suppression part 2.

[0085] Specifically, W2 is the diameter of the side of the first blade 21 and the second blade 22 away from the outer edge 11 of the air inlet 1 when the first blade 21 and the second blade 22 rotate toward the inside of the fan 100. That is, the diameter of the free side of the first blade 21 and the second blade 22 away from the rotating side is W2. By substituting the range of L into W2=D2-2Lcosα, and according to 0.75D1≤D2-2Lcosα≤D1-5mm, the range of W2 is obtained. This avoids the situation where the diameter of the side of the flow suppression part 2 away from the outer edge 11 of the air inlet 1 is too small, which would affect the air intake efficiency of the fan.

[0086] In this embodiment, along the circumferential direction of the outer edge 11 of the air inlet 1, the extension dimension of the first blade 21 corresponds to the central angle θ1, and the extension dimension of the second blade 22 corresponds to the central angle θ2, wherein 0 < θ1 < 30°, and 0.5θ1 ≤ θ2 ≤ 1.5θ1.

[0087] Specifically, the extension dimensions of the first blade 21 and the second blade 22 are arc-shaped. The extension dimensions of the first blade 21 and the second blade 22 along the circumferential direction of the outer edge 11 of the air inlet 1 are limited by the central angle corresponding to the arc-shaped air inlet 1. This prevents the difference in central angles between the extension dimensions of the first blade 21 and the second blade 22 from being too large, which could result in an excessively small maximum turning angle of the flow-damping section 2 towards the fan 100, thus affecting the fan's air intake efficiency. It is understood that the extension dimension of the first blade 21 can be larger than the extension dimension of the second blade 22, and vice versa.

[0088] It is understandable that the range of θ2 can be obtained by substituting the range of θ1 into 0.5θ1≤θ2≤1.5θ1.

[0089] In this embodiment, a first protrusion 211 is provided in the middle area of ​​the first blade 21 facing the outer edge 11 of the air inlet 1, and a second protrusion 221 is provided in the middle area of ​​the second blade 22 facing the outer edge 11 of the air inlet 1. A groove 12 and a rotating shaft 13 are provided on the outer edge 11 of the air inlet 1 corresponding to the first protrusion 211 and the second protrusion 221. The rotating shaft 13 extends from the inner wall of the groove 12 and passes through the first protrusion 211 and the second protrusion 221. Along the circumferential direction of the outer edge 11 of the air inlet 1, the extension dimension of the first protrusion 211 corresponds to a central angle of β1, and the extension dimension of the second protrusion 221 corresponds to a central angle of β2, wherein 0.2θ1≤β1≤0.8θ1, 0.2θ2≤β2≤0.8θ2.

[0090] Specifically, the extension dimensions of the first protrusion 211 and the second protrusion 221 are arc-shaped. The extension dimensions of the first protrusion 211 and the second protrusion 221 are limited along the circumferential direction of the outer edge 11 of the air inlet 1 according to the central angle of the air inlet 1 corresponding to the arc-shaped line. This ensures that the first protrusion 211 and the second protrusion 221 can drive the first blade 21 and the second blade 22 to rotate freely, avoiding the situation where the extension dimensions of the first protrusion 211 and the second protrusion 221 are too small and the bearing capacity is insufficient, causing the first blade 21 and the second blade 22 to fall off after multiple rotations.

[0091] It is understandable that the range of values ​​for θ1 can be obtained by substituting the range of values ​​for θ1 into 0.2θ1≤β1≤0.8θ1. Similarly, the range of values ​​for β2 can be obtained by substituting the range of values ​​for θ2 into 0.2θ2≤β2≤0.8θ2.

[0092] In this embodiment, the extension dimension of the first protrusion 211 or the second protrusion 221 into the groove 12 is L1, wherein 0.1L≤L1≤L2≤0.5L, L2 is the extension length of the limiting part 3 from the outer edge 11 of the air inlet 1 toward the axis of the air inlet 1, and L is the extension length of the flow suppressing part 2 from the outer edge 11 near the air inlet 1 to the outer edge 11 away from the air inlet 1.

[0093] Specifically, the groove 12 is a recessed groove formed by the outer edge 11 to drive the first blade 21 and the second blade 22 to rotate. A rotating shaft 13 is inserted into the groove 12, extending along the circumferential direction of the outer edge 11 and extending out of the inner wall of the groove 12 along the circumferential direction of the outer edge 11. The first protrusion 211 or the second protrusion 221 extends into the groove 12 and has a through hole along the circumferential direction of the outer edge 11. The rotating shaft 13 passes through the through hole so that the first blade 21 with the first protrusion 211 and the second blade 22 with the second protrusion 221 can be rotatably connected to the outer edge 1. By substituting the value range of L into 0.1L≤L1≤L2≤0.5L, the value range of L1 is obtained. Furthermore, by limiting the extension dimension of the first protrusion 211 or the second protrusion 221 into the groove 12, the load-bearing capacity of the first protrusion 211 or the second protrusion 221 is further guaranteed.

[0094] Furthermore, since L2 is greater than or equal to L1, the extension dimension of the limiting part 3 is limited to prevent the extension dimension of the limiting part 3 from being too large, which would reduce the diameter of the air inlet 1 used for air intake of the fan 100, thereby ensuring the performance of the fan 100.

[0095] This embodiment also provides an anti-backflow fan, which includes the backflow suppression device described above. The backflow suppression part 2 and the limiting part 3 work together to reduce the backflow of gas when there is local positive pressure at the air inlet 1. No additional detection mechanism and drive mechanism are required. The rotation of the suppression part follows the gas flow state, which is lower in cost and more timely in response. It reduces repeated work, thereby improving the efficiency of the fan 100 and reducing energy consumption.

[0096] In addition, this embodiment also provides a refrigerator that includes the aforementioned anti-backflow fan. The anti-backflow fan's ability to suppress gas backflow reduces backflow eddies and lowers the noise of the fan 100 itself. At the same time, the refrigerator with the anti-backflow fan provides more sufficient and more uniform airflow to each compartment, avoiding localized frost formation due to uneven airflow on the evaporator surface of the refrigerator.

[0097] In addition, the refrigerator in this embodiment can also be controlled by a voice module. The refrigerator panel can be equipped with a controller, a voice receiving module, and a voice parsing module, which are based on existing technologies. The voice receiving module receives the user's commands, and the voice parsing module parses the commands. Based on the parsed commands, the controller starts or stops the refrigerator accordingly, thereby realizing intelligent control of the refrigerator and improving the user experience.

[0098] While specific embodiments of the present invention have been described above, those skilled in the art should understand that these are merely illustrative examples, and the scope of protection of the present invention is defined by the appended claims. Those skilled in the art can make various changes or modifications to these embodiments without departing from the principles and essence of the present invention, but all such changes and modifications fall within the scope of protection of the present invention.

Claims

1. A backflow suppression device, wherein the backflow suppression device is used to suppress the backflow of gas at the air inlet of a fan to outside the fan, characterized in that, The backflow suppression device includes: A flow-suppressing part is provided around the outer edge of the air inlet. One side of the flow-suppressing part is rotatably connected to the outer edge of the air inlet, and the other side of the flow-suppressing part extends toward the axis of the air inlet. The flow-suppressing part is used to rotate around the outer edge of the air inlet. A limiting part is provided around the outer edge of the air inlet. The limiting part is used to restrict the flow suppressing part from rotating outward from the fan. When the gas in the air inlet flows back, the flow suppressing part rotates toward the limiting part. When the air inlet is receiving air, the flow suppressing part rotates toward the impeller of the fan.

2. The reflux suppression device as described in claim 1, characterized in that, The flow suppression part includes a first blade and a second blade, and multiple first blades and second blades are provided. Along the outer circumferential direction of the air inlet, the first blade is provided with a first overlapping edge corresponding to the end of the second blade, and the second blade is provided with a second overlapping edge corresponding to the end of the first blade. The first overlapping edge and the second overlapping edge overlap each other and are staggered along the thickness direction of the first blade or the second blade. The end of the first overlapping edge is spaced apart from the body of the second blade, and the end of the second overlapping edge is spaced apart from the body of the first blade. When air enters the air inlet and gas backflow occurs in a local area of ​​the outer edge of the air inlet, the first blade corresponding to the gas backflow area drives the second blade to rotate toward the limiting part, while the first blade in the remaining area drives the second blade to rotate toward the impeller of the fan. When air enters through the air inlet and gas backflow occurs in all areas of the outer edge of the air inlet, all the first blades and the second blades rotate toward the limiting part simultaneously. When air enters through the air inlet and no gas backflow occurs in any area of ​​the outer edge of the air inlet, all the first blades and the second blades rotate toward the impeller of the fan.

3. The reflux suppression device as described in claim 2, characterized in that, The surface of the first overlapping edge, which is used to overlap the second overlapping edge, extends from the main body of the first blade to the middle area of ​​the first overlapping edge and is provided with an inclined slope or an arc-shaped slope. Alternatively, the surface of the second overlapping edge used to overlap the first overlapping edge extends from the body of the second blade to the middle area of ​​the second overlapping edge and is provided with an inclined slope or an arc-shaped slope.

4. The reflux suppression device as described in claim 3, characterized in that, The first blade and the second blade extend the same length from the outer edge of the air inlet toward the axis of the air inlet. When air enters through the air inlet, the angle between the first blade and the second blade and the limiting part is α, where 10°≤α≤80°.

5. The reflux suppression device as described in claim 4, characterized in that, When air enters through the air inlet and no gas backflow occurs in any area of ​​the outer edge of the air inlet, the distance between the first blade and the second blade on the outer edge away from the air inlet and the impeller of the fan along the axial direction of the fan is W1, where W1 = H - Lsinα ≥ 5 mm. When air enters through the air inlet and no gas backflow occurs in any area of ​​the outer edge of the air inlet, the diameter of the first blade and the second blade on the outer edge away from the air inlet along the radial direction of the fan is W2, where W2 = D2 - 2Lcosα, and the value range of W2 is 0.75D1 ≤ D2 - 2Lcosα ≤ D1 - 5mm. Here, H is the axial distance from the outer edge end of the fan impeller near the air inlet to the outer edge of the first blade and the second blade facing the air inlet, L is the extension length of the flow suppression part from the outer edge near the air inlet to the outer edge away from the air inlet, D1 is the outer edge diameter of the fan impeller, and D2 is the outer edge diameter of the flow suppression part.

6. The reflux suppression device as described in claim 2, characterized in that, Along the outer circumferential direction of the air inlet, the central angle corresponding to the extension dimension of the first blade is θ1, and the central angle corresponding to the extension dimension of the second blade is θ2, wherein 0 < θ1 < 30°, and 0.5θ1 ≤ θ2 ≤ 1.5θ1.

7. The reflux suppression device as described in claim 6, characterized in that, The first blade has a first protrusion in the middle area of ​​the side facing the outer edge of the air inlet, and the second blade has a second protrusion in the middle area of ​​the side facing the outer edge of the air inlet. The outer edge of the air inlet has a groove and a rotating shaft corresponding to the first and second protrusions. The rotating shaft extends from the inner wall of the groove and passes through the first and second protrusions. Along the circumferential direction of the outer edge of the air inlet, the extension dimension of the first protrusion corresponds to a central angle β1, and the extension dimension of the second protrusion corresponds to a central angle β2, wherein 0.2θ1≤β1≤0.8θ1, 0.2θ2≤β2≤0.8θ2.

8. The reflux suppression device as described in claim 7, characterized in that, The extension dimension of the first protrusion or the second protrusion into the groove is L1, wherein 0.1L≤L1≤L2≤0.5L, L2 is the extension length of the limiting part from the outer edge of the air inlet toward the axis of the air inlet, and L is the extension length of the flow suppressing part from the outer edge near the air inlet to the outer edge away from the air inlet.

9. A backflow prevention fan, characterized in that, The anti-backflow fan includes the backflow suppression device as described in any one of claims 1-8.

10. A refrigerator, characterized in that, The refrigerator includes the anti-backflow fan as described in claim 9.

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