An impeller and fan for an ironing machine adsorption fan

Abstract

This application relates to an impeller and fan for an ironing machine's adsorption fan, belonging to the field of ironing machines. It includes a hub, a rear wall, and multiple blades. The hub has a central hole, and the multiple blades are arranged on the rear wall to form a semi-open impeller structure. The blades are bent from the inlet end to the outlet end in a direction opposite to the impeller's rotation direction. The blade inlet angle β1 is 44°–47°, and the outlet angle β2 is 47°–48°, with β1 < β2. The fan includes a volute, a drive component, and the aforementioned impeller. The volute includes an air inlet, a centrifugal chamber, an air outlet, and a guide tube section. This application can improve the flow state within the impeller's airflow channel, reduce inlet impact, outlet wake disturbance, and eddy noise, and improve the negative pressure build-up capability of the ironing machine's adsorption fan.

Description

Technical Field

[0001] This application relates to the field of ironing machines, and in particular to an impeller and fan for an ironing machine's adsorption fan. Background Technology

[0002] In home or commercial ironing equipment, a suction fan is typically installed below the ironing table to ensure garments adhere smoothly and evenly during ironing. This suction fan creates effective negative pressure at the table surface, guaranteeing a tight seal between the garments and the ironing surface and minimizing shifting, wrinkling, or curling. The suction fan's ability to build up negative pressure directly affects the stability of garment adhesion, while the noise generated during operation can also impact the user experience.

[0003] Most existing ironing machine suction fans employ an axial impeller combined with a cylindrical air duct structure. The high-speed rotation of the impeller generates axial airflow to achieve suction. To meet suction volume or negative pressure requirements, these impellers typically need to operate at higher speeds, resulting in weak negative pressure capacity. Airflow separation, backflow, and impact easily occur at the blade inlet, blade outlet, and air duct transition areas, generating eddy noise and pressure pulsation, leading to significant fan noise. Adding additional silencing structures to reduce noise would increase the complexity of the air duct structure and the overall space occupied by the machine.

[0004] Centrifugal impellers are gradually being adopted. Adjusting the inlet tilt angle of the blades regulates the airflow's incidence as it enters the airflow channel, reducing impact and separation at the blade leading edge. Adjusting the outlet tilt angle regulates the airflow's exit direction, reducing wake disturbance at the blade trailing edge and interference between the outlet airflow and the fan casing. This reduces airflow pulsation and eddy noise during impeller operation. However, the wide range of selectable inlet and outlet tilt angles for existing blades makes it difficult to achieve a proper match. This results in airflow not flowing smoothly along the airflow channel formed by the blades, easily causing inlet impact and flow separation at the inlet, and wake disturbance and outlet pressure pulsation at the outlet, thus increasing aerodynamic noise during impeller operation.

[0005] Optimizing the matching relationship between the inlet and outlet tilt angles of the blades to reduce the noise generated by the impeller has become an urgent problem for those skilled in the art. Summary of the Invention

[0006] In order to optimize the matching relationship between the inlet tilt angle and the outlet tilt angle of the blades and reduce the noise generated by the impeller, this application provides an impeller and a fan for an ironing machine adsorption fan.

[0007] On the one hand, the technical solution provided in this application for an adsorption fan impeller of an ironing machine adopts the following: An impeller for an ironing machine's adsorption fan includes a hub, a rear wall, and multiple blades. The hub has a central hole for connecting with a drive component, and the multiple blades are disposed on the rear wall, so that the impeller forms a semi-open impeller structure. The blades are bent from the air inlet end to the air outlet end in a direction opposite to the rotation direction of the impeller; The inlet angle of the blade is the inlet angle β1, and the outlet angle of the blade is the outlet angle β2, where β1 < β2, the value of β1 ranges from 44° to 47°, and the value of β2 ranges from 47° to 48°.

[0008] By adopting the above technical solution, the impeller is formed into a semi-open structure, allowing airflow to enter the airflow channel between adjacent blades from the open side of the impeller and be discharged to the outer periphery of the impeller under the guidance of the blades. The blades are bent from the inlet end to the outlet end in a direction opposite to the impeller rotation direction, forming a backward guiding structure, which helps to reduce blade load and airflow impact at the outlet. By limiting the inlet angle β1 to 44°~47° and the outlet angle β2 to 47°~48°, and making β1<β2, the airflow can have a small inlet impact angle when entering the airflow channel, and a smoother discharge direction when leaving the airflow channel. This reduces flow separation at the inlet end, wake disturbance at the outlet end, and outlet pressure pulsation, thereby reducing aerodynamic noise during impeller operation.

[0009] Preferably, the air inlet end of the blade is provided with an oblique transition section, which is obliquely arranged from the root edge of the blade upward along the airflow direction.

[0010] By adopting the above technical solution, the oblique transition section can pre-guide the intake airflow when the airflow enters the impeller, so that the airflow gradually enters the airflow channel between adjacent blades, reducing the situation where the airflow directly impacts the leading edge of the blade, thereby reducing the intake end vortex and inlet noise.

[0011] Preferably, the blade is arranged perpendicular to the rear wall.

[0012] By adopting the above technical solution, a more stable support relationship is formed between the blade and the rear wall, which is conducive to improving the structural stability of the blade during high-speed rotation and reducing blade wobble or deformation. At the same time, this setting is also conducive to ensuring the positional consistency of multiple blades during impeller forming, while reducing processing difficulty and facilitating processing.

[0013] Preferably, the height of the blade at the air inlet end is T1, the height of the blade at the air outlet end is T2, and T1 is greater than T2.

[0014] By adopting the above technical solutions, the larger blade height at the inlet end can improve the impeller's air intake capacity, allowing the airflow to enter the airflow channel more fully; the smaller blade height at the outlet end can appropriately control the airflow discharge section and the blade outlet load, allowing the airflow to gradually transition during the blade guidance process, reducing abrupt changes in airflow and vortex formation at the outlet, thereby further reducing aerodynamic noise.

[0015] Preferably, T1 is 9mm-10mm and T2 is 7mm-8mm.

[0016] By adopting the above technical solution, the height of the blades at the air inlet and outlet ends is controlled within a range suitable for the small-scale operation of the ironing machine's adsorption fan. This ensures that the impeller can guarantee air intake capacity and negative pressure establishment capacity while avoiding increased resistance due to excessively high blades or insufficient airflow guidance capacity due to excessively low blades.

[0017] Preferably, the hub has a guide section at the air inlet end, the guide section including a conical surface and / or a circular arc transition surface, the guide section being used to guide the airflow entering the impeller to the blades.

[0018] By adopting the above technical solution, the guide section can smoothly guide the airflow entering the central area of ​​the impeller, reduce the backflow and local eddies caused by the airflow directly impacting the hub intake end, and enable the airflow to enter the airflow channel between the blades more smoothly.

[0019] Preferably, the impeller further includes a lip, which is disposed on the side of the blade facing away from the rear wall.

[0020] By adopting the above technical solutions, the lip can improve the overall rigidity of the open side of the impeller and reduce the vibration or deformation of the free end of the blade during high-speed rotation. At the same time, the lip can also serve as a dynamic balancing correction part, which facilitates weight reduction during the dynamic balancing adjustment of the impeller, thereby reducing vibration and noise during impeller operation.

[0021] Preferably, the ratio of the blade diameter D1 to the rear wall outer diameter D2 is 1:1.

[0022] By adopting the above technical solution, the outer edge of the blade and the outer edge of the rear wall are kept consistent in radial dimension, which is conducive to the rear wall providing sufficient support for the blade, while avoiding excessive protrusion of the outer edge of the blade relative to the rear wall, which would cause structural vibration or additional turbulence, and improve the stability of the impeller at high speed.

[0023] This application also provides an adsorption fan for an ironing machine, employing the following technical solution: An adsorption fan for an ironing machine includes a volute, a drive unit, and the aforementioned adsorption fan impeller for an ironing machine. The impeller is disposed inside the volute, and the drive unit is connected to the impeller and is used to drive the impeller to rotate. The volute includes an air inlet, a centrifugal chamber, an air outlet, and a guide tube section. The air inlet is correspondingly arranged to the open side of the impeller. The centrifugal chamber surrounds the outer periphery of the impeller. The air outlet is connected to the guide tube section. The centrifugal chamber is used to collect the centrifugal airflow discharged by the impeller, and the guide tube section is used to guide the centrifugal airflow to discharge.

[0024] By adopting the above technical solution, the drive component drives the impeller to rotate inside the volute. Airflow enters the open side of the impeller through the air inlet and is discharged outward under the action of the blades. The centrifugal chamber collects the centrifugal airflow discharged by the impeller, and the air guide section guides the centrifugal airflow outward. This fan can form a relatively stable negative pressure within the limited space inside the ironing machine to improve the stability of clothing adsorption. At the same time, the airflow turbulence and vortex noise are reduced through the guiding cooperation between the impeller and the volute.

[0025] Preferably, the inner wall of the centrifuge chamber is contoured to the upper edge of the blade, and the gap δ between the upper edge of the blade and the inner wall of the centrifuge chamber is less than 1 mm. And / or, the inlet diameter D3 of the blade is equal to or substantially equal to the inlet diameter D4 of the volute; And / or, the outer diameter D1 of the impeller is 32mm-36mm, and the outlet diameter D5 of the volute is 48mm-52mm.

[0026] By adopting the above technical solution, the centrifuge chamber inner wall and the blades are contour-followingly designed with a gap of less than 1mm, which reduces the leakage of high-pressure airflow from the outer periphery of the impeller to the low-pressure area, reduces gap leakage vortices and leakage noise, and improves the fan's ability to build negative pressure. Matching the blade inlet diameter with the volute inlet diameter reduces abrupt airflow changes and intake losses at the inlet. Setting the impeller outer diameter and volute outlet diameter within the above-mentioned range allows for compact installation within the ironing machine and ensures smoother airflow discharge through the volute.

[0027] In summary, this application includes at least one of the following beneficial technical effects: 1. This application sets the blades as backward-curved blades that bend from the inlet end to the outlet end in a direction opposite to the impeller rotation direction, and limits the inlet angle β1 to 44°~47° and the outlet angle β2 to 47°~48°, so that the inlet and outlet angles of the blades are matched, which can reduce the inlet impact when the airflow enters the blade passage and the wake disturbance when it leaves the blade passage, thereby reducing the aerodynamic noise during the impeller operation. 2. By setting an oblique transition section at the blade inlet end and a guide section with a conical and / or circular arc transition surface at the hub inlet end, this application can pre-guide the airflow entering the impeller, reduce backflow, separation and vortex in the blade leading edge and hub center area, and improve the smoothness of airflow entering the blade passage. 3. This application makes the height T1 of the blade inlet end greater than the height T2 of the outlet end, so that the impeller has a better air intake capacity at the inlet end and reduces the sudden airflow and outlet load at the outlet end, which is beneficial to the stable operation of the impeller under the system resistance conditions of the ironing machine adsorption fan. 4. This application reduces gap leakage and leakage vortex by setting the impeller inside the volute, which includes the air inlet, centrifugal chamber, air outlet and air guide section, and making the inner wall of the centrifugal chamber conform to the contour of the blade and maintain a small gap fit, thereby improving the negative pressure build-up capability and reducing the operating noise of the fan. Attached Figure Description

[0028] Figure 1 This is a schematic diagram of the structure of an adsorption fan impeller for an ironing machine according to an embodiment of this application.

[0029] Figure 2 It is a display Figure 1 Front view of the middle impeller structure.

[0030] Figure 3 It is along Figure 2 A cross-sectional view along line AA in the middle.

[0031] Figure 4 This is a schematic diagram illustrating the structure of an adsorption fan used in an ironing machine.

[0032] Explanation of reference numerals in the attached drawings: 1. Impeller; 11. Hub; 12. Rear wall; 13. Blade; 14. Center hole; 15. Oblique transition section; 16. Root edge; 17. Upper edge; 18. Guide section; 19. Lip; 2. Volute; 21. Air inlet; 22. Centrifugal chamber; 23. Air outlet; 24. Air guide section. Detailed Implementation

[0033] The following is in conjunction with the appendix Figure 1-4 This application will be described in further detail.

[0034] This application provides a technical solution for an ironing machine adsorption fan impeller using the following method.

[0035] Reference Figure 1An impeller for an ironing machine's suction fan includes a hub 11, a rear wall 12, and multiple blades 13. The hub 11 is located in the center of the impeller and has a central hole 14 for connecting to the output shaft of a drive component, enabling the drive component to drive the impeller to rotate around its own axis. The rear wall 12 is located on the outer periphery of the hub 11. In this embodiment, the rear wall 12 has a curved surface structure. Specifically, the distance from the rear wall 12 to the central axis of the hub 11 gradually increases from the air inlet end to the air outlet end of the hub 11.

[0036] Multiple blades 13 are disposed on the rear wall 12 and are distributed at intervals along the circumference of the impeller. In this embodiment, nine blades 13 are used as an example. All nine blades 13 are disposed on one side of the rear wall 12, so that the impeller forms a semi-open impeller structure, and the airflow can enter the airflow channel between two adjacent blades 13 from the open side.

[0037] Reference Figure 1 , Figure 2 The blade 13 has an inlet end and an outlet end. The inlet end is close to the air intake area of ​​the impeller, and the outlet end is close to the outer peripheral exhaust area of ​​the impeller. The blade 13 is bent from the inlet end to the outlet end in a direction opposite to the rotation direction of the impeller, thus forming a backward-curved blade 13. The inlet end tilt angle of the blade 13 is the inlet angle β1, and the outlet end tilt angle of the blade 13 is the outlet angle β2. The inlet angle β1 is smaller than the outlet angle β2. The value of the inlet angle β1 ranges from 44° to 47°, and the value of the outlet angle β2 ranges from 47° to 48°.

[0038] By setting the blade 13 as a backward-curved blade and making the inlet angle β1 and outlet angle β2 match as described above, the airflow can have a smaller inlet impact angle when entering the airflow channel between adjacent blades 13, and at the same time, the airflow can have a smoother discharge direction when leaving the airflow channel, thereby reducing flow separation at the inlet end, wake disturbance at the outlet end, and outlet pressure pulsation, and reducing aerodynamic noise during impeller operation.

[0039] In this embodiment, by setting the number of blades 13 to nine, and in conjunction with the aforementioned inlet angle β1 and outlet angle β2 ranges, the impeller can achieve better air intake capacity and lower aerodynamic noise under the miniaturized and high-speed operating conditions of the ironing machine adsorption fan.

[0040] The inlet end of blade 13 is provided with an inclined transition section 15, which is inclined from the root edge 16 to the upper edge 17 of blade 13 along the airflow direction. The root edge 16 is the edge of blade 13 near the rear wall 12, and the upper edge 17 is the edge of blade 13 away from the rear wall 12. When the airflow enters the impeller, the inclined transition section 15 can pre-guide the airflow, so that the airflow gradually enters the airflow channel between two adjacent blades 13, reducing the direct impact of airflow on the leading edge of blade 13, thereby reducing inlet vortex and inlet noise.

[0041] The blade 13 is perpendicular to the rear wall 12. Specifically, the surface of the blade 13 is perpendicular or substantially perpendicular to the rear wall 12. This arrangement provides a more stable support relationship between the blade 13 and the rear wall 12, which helps improve the blade 13's resistance to deformation during high-speed rotation. It also helps ensure the positional consistency of multiple blades 13 during impeller injection molding, reducing vibration and noise caused by blade 13 molding deviations or rotational imbalances. Furthermore, it reduces the difficulty of impeller machining and improves the ease of impeller processing.

[0042] Reference Figure 1 , Figure 3 The blade 13 has a first height T1 at the inlet end and a second height T2 at the outlet end, with the first height T1 being greater than the second height T2. Preferably, the first height T1 = 9mm to 10mm and the second height T2 = 7mm to 8mm. This configuration allows the blade 13 to have good wind-catching and intake capabilities at the inlet end, while appropriately reducing the outlet load at the outlet end, resulting in a smoother airflow from the impeller and reduced outlet eddies and pressure pulsations.

[0043] The hub 11 has a guide section 18 in the area formed between the air inlet ends of multiple blades 13. The guide section 18 may include a conical surface, an arc transition surface, or both. The guide section 18 is used to guide the airflow entering the central region of the impeller to the blades 13, reducing the impact, backflow, and vortex generated by the airflow at the air inlet end of the hub 11.

[0044] The impeller also includes a lip 19, which is fixedly installed on the side of the hub 11 away from the rear wall 12. The lip 19 extends circumferentially along the impeller and can improve the structural rigidity of the open side of the blade 13, reducing the vibration risk at the free end of the blade 13 during high-speed rotation. At the same time, the lip 19 can also serve as a weight-reducing part during impeller dynamic balancing correction, so as to improve the dynamic balance performance of the impeller during high-speed rotation.

[0045] In this embodiment, the ratio of the blade diameter D1 to the impeller rear wall 12 outer diameter D2 is 1:1, meaning that the outer circumferential diameter of the blade 13 is equal to or substantially equal to the outer circumferential diameter of the rear wall 12. Therefore, the rear wall 12 can provide sufficient support for the blade 13, preventing the outer edge of the blade 13 from excessively protruding relative to the rear wall 12 and thus avoiding additional turbulence or structural vibration.

[0046] The impeller can be made of high-temperature resistant plastic, and the hub 11, rear wall 12, blades 13, and lip 19 can be integrally molded by injection molding. Using high-temperature resistant plastic can adapt to the relatively high operating temperature environment inside the ironing machine; injection molding can reduce the cost of mass production of the impeller and improve the molding consistency among multiple blades 13.

[0047] The implementation principle of the adsorption fan impeller for an ironing machine according to an embodiment of this application is as follows: the airflow enters from the open side of the impeller and flows to the area where multiple blades 13 are located under the guidance of the air inlet guide section 18 of the hub 11; at the same time, the oblique transition section 15 of the air inlet end of the blade 13 pre-guides the airflow before it enters the blade passage, so that the airflow enters the airflow channel formed between two adjacent blades 13 more smoothly, reducing the inlet impact and local vortex caused by the airflow directly impacting the leading edge of the blade 13.

[0048] After the airflow enters the blade passage, the blade 13 bends from the inlet end to the outlet end in a direction opposite to the impeller rotation direction, forming a backward-directing flow structure. Since the inlet angle β1 of the blade 13 is limited to 44° to 47° and the outlet angle β2 is limited to 47° to 48°, and β1 < β2, the airflow can better conform to the guiding direction of the blade 13 when it enters the blade passage from the inlet end, and gradually transitions to the outlet end within the blade passage, reducing flow separation within the blade passage; when the airflow exits from the outlet end, its exit direction is also relatively smooth, thereby reducing wake disturbance at the trailing edge of the blade 13 and outlet pressure pulsation.

[0049] Meanwhile, the height of the blade 13 at the inlet end is greater than that at the outlet end, giving the inlet end of the blade 13 better intake capacity, while the outlet end can appropriately reduce the outlet load, reducing abrupt changes and vortex formation during airflow discharge. The blade 13 is set perpendicular to the rear wall 12, which can improve the connection stability between the blade 13 and the rear wall 12 and reduce the sway and deformation of the blade 13 during high-speed rotation; the lip 19 is set on the side of the blade 13 away from the rear wall 12, which can enhance the overall rigidity of the impeller and facilitate dynamic balancing to reduce weight, thereby reducing vibration noise during high-speed operation of the impeller.

[0050] Therefore, during the rotation of the impeller in this embodiment, the airflow can flow relatively smoothly from the inlet end to the outlet end within the impeller through the combined action of the guide section 18, the oblique transition section 15, the backward blades 13, the matching relationship between the inlet angle β1 and the outlet angle β2, and the height difference of the blades 13. Under centrifugal force, the airflow is discharged to the outer periphery of the impeller. This ensures the negative pressure building capability of the adsorption fan while reducing inlet impact, flow separation, wake disturbance, outlet pressure pulsation, and noise caused by structural vibration.

[0051] This application also discloses an adsorption fan for an ironing machine.

[0052] Reference Figure 4 An adsorption fan for an ironing machine includes a volute 2, a drive component, and the aforementioned impeller 1. The impeller 1 is disposed within the volute 2, and the drive component is connected to the impeller 1 and drives the impeller 1 to rotate.

[0053] The volute 2 includes an air inlet 21, a centrifugal chamber 22, an air outlet 23, and a guide tube section 24. The air inlet 21 is positioned corresponding to the open side of the impeller 1, allowing external airflow to enter the impeller 1 through the air inlet 21. The centrifugal chamber 22 surrounds the outer periphery of the impeller 1 and is used to collect the centrifugal airflow discharged from the impeller 1. The air outlet 23 communicates with the centrifugal chamber 22, and the guide tube section 24 communicates with the air outlet 23, guiding the airflow collected in the centrifugal chamber 22 to discharge.

[0054] The inner wall of the centrifuge chamber 22 is contoured to the upper edge 17 of the blade 13, and the gap δ between the upper edge 17 of the blade 13 and the inner wall of the centrifuge chamber 22 is less than 1 mm. This design reduces the backflow of high-pressure airflow from the outer periphery of the impeller 1 to the low-pressure area through the gap, reduces gap leakage flow and leakage vortex, improves the negative pressure build-up capability of the adsorption fan, and reduces noise caused by gap leakage.

[0055] In this embodiment, the inlet diameter of the blade 13 is equal to or substantially equal to the diameter of the air inlet 21 of the volute 2. As a result, when the airflow enters the impeller 1 from the air inlet 21, the airflow contraction, expansion, and intake loss caused by abrupt changes in size can be reduced, making the intake process smoother.

[0056] The impeller 1 has a diameter D1 of 32–36 mm; the outlet 23 of the volute 2 has a diameter D5 of 48–52 mm; and the depth H of the impeller hub 11 relative to the outlet 23 of the volute 2 is greater than 5 mm. This arrangement effectively guides the centrifugal airflow from radial to axial directions. Furthermore, the resulting axial airflow can carry away heat from the drive motor, which is beneficial for its heat dissipation.

[0057] To verify the impact of the inlet angle β1 and outlet angle β2 of blade 13 on the noise of impeller 1, and since impeller 1 cannot operate independently, impeller 1 was assembled with volute 2 for testing. Specifically, while keeping other parameters of blade 13 constant, experiments were conducted on different combinations of inlet angle β1 and outlet angle β2 by changing the sizes of the inlet angle β1 and outlet angle β2 of blade 13, under the conditions of impeller 1 speed of 46000 rpm, 10 m³ / h, and the detection point being 0.5 m in the forward direction of air outlet 23. In Example 1, the inlet angle β1 is 44°, the outlet angle β2 is 47°, and the impeller noise is 77.8dB.

[0058] In Example 2, the inlet angle β1 is 45°, the outlet angle β2 is 47°, and the impeller noise is 76.4dB.

[0059] In Example 3, the inlet angle β1 is 45°, the outlet angle β2 is 48°, and the impeller noise is 77.0dB.

[0060] In Example 4, the inlet angle β1 is 47°, the outlet angle β2 is 48°, and the impeller noise is 76.8dB.

[0061] As can be seen from the above embodiments, when the inlet angle β1 is in the range of 44° to 47° and the outlet angle β2 is in the range of 47° to 48°, the noise of impeller 1 under the same speed and flow conditions is maintained at 76.4dB to 77.8dB, and the overall noise is low. This indicates that the range of inlet angle β1 and outlet angle β2 can form a good angle matching relationship, so that the airflow has a relatively smooth flow state at both the inlet and outlet ends of blade 13.

[0062] To further illustrate the effect of the aforementioned angle range, several comparative scales are set up.

[0063] In Comparative Example 1, the inlet angle β1 is 40° and the outlet angle β2 is 47°, where the inlet angle β1 is below the range defined in this application. The impeller 1 noise level is 84.8 dB. This result indicates that when the inlet angle β1 is too small, the airflow entering the airflow channel between adjacent blades 13 is prone to deviating from the guide direction of blade 13, resulting in enhanced inlet impact and flow separation at the inlet end, leading to increased noise.

[0064] In Comparative Example 2, the inlet angle β1 is 42° and the outlet angle β2 is 47°, where the inlet angle β1 is below the range defined in this application. Under the same conditions, the impeller 1 noise is 82.3 dB. This result indicates that when the inlet angle β1 is below 44°, although the outlet angle β2 is within the range defined in this application, the airflow guidance at the inlet end is still not ideal, and the airflow is prone to generate local vortices at the leading edge of the blade 13, thus leading to increased noise.

[0065] In Comparative Example 3, the inlet angle β1 is 49° and the outlet angle β2 is 48°, where the inlet angle β1 is higher than the range defined in this application and the inlet angle β1 is greater than the outlet angle β2. Under the same conditions, the impeller noise is 83.6 dB. This result indicates that when the inlet angle β1 is too large and disrupts the matching relationship that the inlet angle β1 is smaller than the outlet angle β2, the flow transition between the inlet and outlet ends of the blade 13 is not smooth enough, which easily leads to flow separation and pressure pulsation.

[0066] In Comparative Example 4, the inlet angle β1 is 45° and the outlet angle β2 is 45°, where the outlet angle β2 is below the range defined in this application. Under the same conditions, the impeller noise is 85.2 dB. This result indicates that when the outlet angle β2 is too small, the discharge direction of the airflow leaving the airflow channel of blade 13 is restricted, which easily forms a wake disturbance at the trailing edge of blade 13, resulting in increased outlet noise.

[0067] In Comparative Example 5, the inlet angle β1 is 45° and the outlet angle β2 is 52°, where the outlet angle β2 is higher than the range defined in this application. Under the same conditions, the impeller 1 noise is 86.7 dB. This result indicates that when the outlet angle β2 is too large, the change in direction of the airflow as it leaves the airflow channel increases, the pressure pulsation and wake disturbance at the outlet end are enhanced, and thus the noise increases.

[0068] In Comparative Example 6, the inlet angle β1 was 45° and the outlet angle β2 was 65°, with the outlet angle β2 significantly exceeding the range defined in this application. The impeller noise was 96.1 dB. This result indicates that when the outlet angle β2 significantly deviates from the range defined in this application, the airflow discharge state at the outlet end of blade 13 deteriorates significantly, and the outlet pressure pulsation and vortex noise increase significantly.

[0069] The experimental results of the above embodiments and comparative examples are shown in the table below: type β1 / ° β2 / ° Noise / dB Example 1 44 47 77.8 Example 2 45 47 76.4 Example 3 45 48 77.0 Example 4 47 48 76.8 Comparative Example 1 40 47 84.8 Comparative Example 2 42 47 82.3 Comparative Example 3 49 48 83.6 Comparative Example 4 45 45 85.2 Comparative Example 5 45 52 86.7 Comparative Example 6 45 65 96.1 As shown in the table above, within the range of inlet angle β1 of 44° to 47° and outlet angle β2 of 47° to 48°, the noise of impeller 1 is significantly lower than that of the comparative examples. This indicates that the inlet angle β1 and outlet angle β2 of blade 13 are not arbitrarily selected in this application, but rather, by limiting the inlet angle β1 and outlet angle β2 to a narrower matching range, a better transition relationship is formed between the airflow at the inlet end and the outlet end of blade 13, thereby reducing inlet impact, flow separation, wake disturbance, and outlet pressure pulsation, and achieving a better noise reduction effect.

[0070] The above are all preferred embodiments of this application, and are not intended to limit the scope of protection of this application. Therefore, all equivalent changes made in accordance with the structure, shape and principle of this application should be covered within the scope of protection of this application.

Claims

1. An impeller for an adsorption fan in an ironing machine, characterized in that: It includes a hub (11), a rear wall (12) and multiple blades (13). The hub (11) is provided with a central hole (14) for connecting with a drive component. The multiple blades (13) are disposed on the rear wall (12), so that the impeller (1) forms a semi-open impeller (1) structure. The blade (13) bends from the air inlet end to the air outlet end in a direction opposite to the rotation direction of the impeller (1); The inlet angle of the blade (13) is the inlet angle β1, and the outlet angle of the blade (13) is the outlet angle β2, where β1 < β2, the value of β1 is in the range of 44° to 47°, and the value of β2 is in the range of 47° to 48°.

2. The impeller for an ironing machine adsorption fan according to claim 1, characterized in that: The air inlet end of the blade (13) is provided with an oblique transition section (15), which is obliquely arranged from the root edge (16) of the blade (13) upward along (17) along the airflow direction.

3. The impeller for an ironing machine adsorption fan according to claim 1, characterized in that: The blade (13) is arranged perpendicularly to the rear wall (12).

4. The impeller for an adsorption fan in an ironing machine according to claim 1, characterized in that: The height of the blade (13) at the air inlet end is T1, and the height of the blade (13) at the air outlet end is T2, and T1 is greater than T2.

5. The impeller for an ironing machine adsorption fan according to claim 4, characterized in that: The T1 is 9mm-10mm, and the T2 is 7mm-8mm.

6. The impeller for an adsorption fan in an ironing machine according to claim 1, characterized in that: The hub (11) is provided with a guide section (18) at the air inlet end. The guide section (18) includes a conical surface and / or a circular arc transition surface. The guide section (18) is used to guide the airflow entering the impeller (1) to the blade (13).

7. The impeller for an adsorption fan in an ironing machine according to claim 1, characterized in that: The impeller also includes a lip (19) disposed on the side of the blade (13) away from the rear wall (12).

8. The impeller for an ironing machine adsorption fan according to claim 1, characterized in that: The ratio of the diameter D1 of the blade (13) to the outer diameter D2 of the rear wall (12) is 1:

1.

9. An adsorption fan for an ironing machine, characterized in that: Includes a volute (2), a drive unit, and an impeller for an ironing machine adsorption fan as described in any one of claims 1-8, wherein the impeller (1) is disposed within the volute (2), and the drive unit is connected to the impeller (1) and is used to drive the impeller (1) to rotate; The volute (2) includes an air inlet (21), a centrifugal chamber (22), an air outlet (23), and a guide tube section (24). The air inlet (21) is disposed corresponding to the open side of the impeller (1). The centrifugal chamber (22) surrounds the outer periphery of the impeller (1). The air outlet (23) is connected to the guide tube section (24). The centrifugal chamber (22) is used to collect the centrifugal airflow discharged from the impeller (1), and the guide tube section (24) is used to guide the centrifugal airflow to discharge.

10. The adsorption fan for an ironing machine according to claim 9, characterized in that: The inner wall of the centrifuge chamber (22) is contoured to the upper edge (17) of the blade (13), and the gap δ between the upper edge (17) of the blade (13) and the inner wall of the centrifuge chamber (22) is less than 1 mm. And / or, the inlet diameter D3 of the blade (13) is equal to or substantially equal to the diameter D4 of the air inlet (21) of the volute (2); And / or, the outer diameter D1 of the impeller (1) is 32mm-36mm, and the diameter D5 of the air outlet (23) of the volute (2) is 48mm-52mm.

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