Fan and ventilation therapy device

Abstract

This application relates to the field of fan technology and discloses a fan and a ventilation therapy device. The fan of this application includes a volute, an impeller, and a baffle. The volute has an air inlet channel, a cavity, and an air outlet channel. The air inlet channel and the air outlet channel are connected through the cavity. The impeller and the baffle are respectively installed in the cavity and spaced apart from the inner wall of the volute. The baffle is located on the side of the impeller away from the air inlet channel. The gap width E between the impeller and the volute, and the gap width H between the baffle and the inner wall of the volute, satisfy: 0.95H≤E≤8H; and / or, the gap area S1 between the impeller and the volute, and the gap area S2 between the baffle and the inner wall of the volute, satisfy: 0.95S2≤S1≤8S2. Through the above technical solution, the fan can achieve good noise reduction performance while meeting the flow requirements.

Description

Technical Field

[0001] This utility model relates to the field of fan technology, specifically to a fan. Furthermore, this utility model also relates to a ventilation therapy device. Background Technology

[0002] Respiratory products, such as ventilators, are used to deliver gas to users. They typically contain a fan to control the flow and pressure of the gas. However, existing fans tend to generate significant noise during operation, affecting the sleep and rest of users or people around the device, and even making it difficult for people to fall asleep, resulting in a poor user experience. Utility Model Content

[0003] The purpose of this invention is to overcome the technical problem of excessive noise during operation of existing fans.

[0004] To achieve the above objectives, the first aspect of this utility model provides a fan, including a volute, an impeller, and a baffle plate. The volute has an air inlet channel, a cavity, and an air outlet channel. The air inlet channel and the air outlet channel are connected through the cavity. The impeller and the baffle plate are respectively installed in the cavity and spaced apart from the inner wall of the volute. The baffle plate is located on the side of the impeller away from the air inlet channel. The gap width E between the impeller and the volute, and the gap width H between the baffle plate and the inner wall of the volute satisfy: 0.95H≤E≤8H; and / or, the gap area S1 between the impeller and the volute, and the gap area S2 between the baffle plate and the inner wall of the volute satisfy: 0.95S2≤S1≤8S2.

[0005] In some embodiments, the gap width E between the impeller and the volute, and the gap width H between the partition and the inner wall of the volute, satisfy: H < E ≤ 6H; and / or, the gap area S1 between the impeller and the volute, and the gap area S2 between the partition and the inner wall of the volute, satisfy: S2 < S1 ≤ 6S2.

[0006] In some embodiments, the gap width E between the impeller and the volute is set to 1.5mm-6mm; and / or, the gap width H between the partition and the inner wall of the volute is set to 0.5-2mm.

[0007] In some embodiments, the gap area S2 between the baffle and the inner wall of the volute is satisfied with the outflow area S3 of the impeller's outlet: 1.5S3≤S2≤2.5S3.

[0008] In some embodiments, the baffle and the impeller are spaced apart along the axial direction of the volute, and the axial distance G between the opposing surfaces of the baffle and the impeller is set to 0.3-5 mm.

[0009] In some embodiments, the partition is located on the side of the air outlet duct closer to the air inlet duct.

[0010] In some embodiments, the axial distance A between the surface of the partition away from the air outlet channel and the top edge of the air outlet channel near the air inlet channel does not exceed 10 mm.

[0011] In some embodiments, the outlet end face of the air inlet channel is higher than the inlet end face of the impeller and has a first axial gap with the inlet end face of the impeller; and / or, the outer edge of the outlet end face of the air inlet channel is located inside the inlet end face and has a second radial gap with the inner edge of the inlet end face.

[0012] In some embodiments, the axial spacing B of the first gap does not exceed 10 mm; and / or, the radial spacing C of the second gap does not exceed 5 mm.

[0013] In some embodiments, the air inlet channel is formed as a tapering channel in the direction close to the impeller, and at least the air inlet inner wall surface of the air inlet channel near the cavity is inclined outward relative to the central axis of the air inlet channel to form a guide structure.

[0014] In some embodiments, the angle between the inner wall surface of the air inlet channel and the central axis of the air inlet channel does not exceed 45°.

[0015] In some embodiments, the fan satisfies at least one of the following conditions: The diameter of the impeller is set to 40-55mm; The diameter of the impeller is set to be 8-25 times the gap width E between the impeller and the volute. The height F of the impeller outlet is set to 0.3-10mm; The inlet diameter of the impeller is set to 10-20mm; The outer diameter of the fan is set to 50-70mm.

[0016] The second aspect of this utility model provides a ventilation therapy device, including the aforementioned fan.

[0017] In the fan provided by this utility model, a baffle is provided on the side of the impeller away from the air inlet channel. The baffle is spaced apart from the inner wall of the volute to form a noise reduction channel. The airflow generated by the impeller's operation flows through the air outlet to the space between the impeller and the volute, and then flows away from the air inlet channel through the noise reduction channel, for example, towards the air outlet channel. When the airflow passes through the noise reduction channel, it can be rectified by the baffle, changing the gas flow state from turbulent to laminar flow, thereby reducing the noise of the airflow.

[0018] The noise reduction channel formed by the alternating partition and the inner wall of the volute affects the fan's output flow rate and noise level. If the noise reduction channel is too small—for example, if the gap width E between the impeller and the volute is greater than 8 times the gap width H between the partition and the inner wall of the volute, or if the gap area S1 between the impeller and the volute is greater than 8 times the gap area S2 between the partition and the inner wall of the volute—the flow resistance through the noise reduction channel is too high, restricting airflow and causing the fan performance to fail to meet the operating flow rate requirements. Conversely, if the noise reduction channel is too large—for example, if the gap width E between the impeller and the volute is less than 0.95 times the gap width H between the partition and the inner wall of the volute, or if the gap area S1 between the impeller and the volute is less than 0.95 times the gap area S2 between the partition and the inner wall of the volute—the partition's ability to disturb the airflow output from the impeller's outlet is limited, making it difficult to achieve significant noise reduction, thus causing the fan performance to fail to meet the noise reduction requirements. In this invention, the width of the noise reduction channel, i.e., the gap width H between the baffle and the inner wall of the impeller and the volute, and the gap width E between the impeller and the volute, satisfy: 0.95H≤E≤8H, and / or the flow area of ​​the noise reduction channel, i.e., the gap area S2 between the baffle and the inner wall of the impeller and the volute, and the gap area S1 between the impeller and the volute, satisfy: 0.95S2≤S1≤8S2, when the fan performance can balance the flow demand and the noise demand.

[0019] Other features and advantages of this invention will be described in detail in the following detailed description section. Attached Figure Description

[0020] Figure 1 This is a cross-sectional schematic diagram of the fan provided by this utility model; Figure 2 This is an isometric drawing of the fan provided by this utility model; Figure 3 This is an exploded view of the fan provided by this utility model; Figure 4 yes Figure 2 Top view of a medium-sized fan; Figure 5 yes Figure 4 Schematic diagram of the cross section along the AA direction Figure 6 This is a schematic diagram of the structure of the upper and lower surfaces of the upper volute provided by this utility model; Figure 7 This is a schematic diagram of the structure of the upper and lower surfaces of the impeller provided by this utility model; Figure 8 This is a schematic diagram of the upper and lower surfaces of the partition provided by this utility model.

[0021] Explanation of reference numerals in the attached figures 1-Volume; 101-Outlet end face; 102-Outlet outer edge; 103-Upper wall of air outlet duct; 104-Inner wall of upper volume; 105-Inner wall of air inlet; 106-Air inlet duct; 107-Cavity; 108-Air outlet duct; 2-Impeller; 201-Inlet end face; 202-Inlet inner edge; 203-First outer edge; 204-Air outlet; 205-Lower surface of impeller; 206-Mounting part; 3-Baffle; 301-Upper upper surface of baffle; 302-Second outer edge; 303-Lower surface of baffle; 304-Noise reduction duct; 4-Lower volume; 5-Motor; 6-Upper volume. Detailed Implementation

[0022] The specific embodiments of this utility model will be described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are for illustration and explanation only and are not intended to limit the scope of this utility model.

[0023] In this utility model, unless otherwise stated, the terms "upper," "lower," "left," "right," "inner," "outer," "top," and "bottom," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0024] Furthermore, in the description of this utility model, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0025] In this utility model, the descriptions using terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples" refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of this utility model. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0026] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between them; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0027] Ventilation therapy equipment, such as home non-invasive ventilators or high-flow humidified oxygen therapy devices, is generally used for respiratory support or assisted ventilation. The fan is one of the core components of the ventilator; adjusting the fan speed can adjust the flow rate or pressure level of gas delivered to the patient. Existing fans generate noise during operation, mainly from motor operation noise and aerodynamic noise generated by airflow passing through the equipment.

[0028] This application provides a fan, see [link to relevant documentation] Figures 1-5 As shown, the fan includes a volute 1, an impeller 2, and a baffle 3. The volute 1 has an air inlet channel 106, a cavity 107, and an air outlet channel 108. The air inlet channel 106 and the air outlet channel 108 are connected via the cavity 107. The impeller 2 and the baffle 3 are respectively installed in the cavity 107 and spaced apart from the inner wall of the volute 1. The baffle 3 is located on the side of the impeller 2 away from the air inlet channel 106. The gap width E between the impeller 2 and the volute 1, and the gap width H between the baffle 3 and the inner wall of the volute 1, satisfy: 0.95H≤E≤8H; and / or, the gap area S1 between the impeller 2 and the volute 1, and the gap area S2 between the baffle 3 and the inner wall of the volute 1, satisfy: 0.95S2≤S1≤8S2.

[0029] The fan provided in this embodiment has a baffle 3 on the side of the impeller 2 away from the air inlet channel 106, and the baffle 3 is spaced apart from the inner wall of the volute 1 to form a noise reduction channel 304. The airflow generated by the rotation of the impeller 2 flows through the air outlet 204 to the space between the impeller 2 and the volute 1, and then flows through the noise reduction channel 304 in a direction away from the air inlet channel 106 (for example, towards the air outlet channel 108). When the airflow flows through the noise reduction channel 304, it can be rectified by the baffle 3 to change the gas flow state, so that the gas flow state changes from turbulent flow to laminar flow, thereby reducing the noise of the gas.

[0030] The size of the noise reduction channel 304 formed by the baffle 3 affects the fan's flow rate and noise. If the size of the noise reduction channel 304 is too small, for example, if the gap width E between the impeller 2 and the volute 1 is more than 8 times the gap width H between the baffle 3 and the inner wall of the volute 1, or if the gap area S1 between the impeller 2 and the volute 1 is more than 8 times the gap area S2 between the baffle 3 and the inner wall of the volute 1, the air resistance at the noise reduction channel 304 will be too large, restricting airflow and causing the fan performance to fail to meet the flow rate requirements. If the size of the noise reduction channel 304 is too large, for example, if the gap width E between the impeller 2 and the volute 1 is less than 0.95 times the gap width H between the baffle 3 and the inner wall of the volute 1, or if the gap area S1 between the impeller 2 and the volute 1 is less than 0.95 times the gap area S2 between the baffle 3 and the inner wall of the volute 1, the baffle 3's rectification capacity for the airflow at the outlet 204 of the impeller 2 will be limited, making it difficult to achieve a significant noise reduction effect, thus causing the fan performance to fail to meet the noise requirements. When the dimensions of the noise reduction channel 304 and the clearance between the impeller 2 and the volute 1 satisfy 0.95H≤E≤8H and / or 0.95S2≤S1≤8S2, the fan performance can balance the flow and noise requirements.

[0031] In some embodiments, the diameter of the baffle 3 can be larger than the diameter of the impeller 2, that is, the gap width E between the impeller 2 and the volute 1 is greater than the gap width H between the baffle 3 and the inner wall of the volute 1 (E>H), or the gap area S1 between the impeller 2 and the volute 1 is greater than the gap area S2 between the baffle 3 and the inner wall of the volute 1 (S1>S2). Thus, the portion of the baffle 3 that extends beyond the outer edge of the impeller 2 can restrict the airflow at the outlet 204 of the impeller 2 from flowing directly downwards. Instead, it needs to be laminated through the reduced-size noise reduction channel 304 to improve the noise reduction effect.

[0032] In some embodiments, the gap width E between the impeller 2 and the volute 1 is no greater than 6 times the gap width H between the baffle 3 and the inner wall of the volute 1; and / or, the gap area S1 between the impeller 2 and the volute 1 is no greater than 6 times the gap area S2 between the baffle 3 and the inner wall of the volute 1. That is, E≤6H or S1≤6S2, so as to maximize the fan flow rate while ensuring good noise reduction effect. In some embodiments, the gap width E and / or area S1 between the impeller 2 and the volute 1 are 1.5-5.5 times the gap width H and / or area S2 between the baffle 3 and the inner wall of the volute 1.

[0033] In some embodiments, the gap width H between the partition 3 and the inner wall of the volute 1 is set to 0.5-2 mm. For example, the gap width H between the partition 3 and the inner wall of the volute 1 is approximately 1 ± 0.5 mm. While maintaining the gap between impeller 2 and volute 1 at 1.9mm-5.5mm (e.g., 1.9mm), the effects of different dimensions of the noise reduction channel 304 on the fan's flow rate and noise reduction performance were tested under a set pressure: When the gap width H between the baffle 3 and the inner wall of volute 1 is less than 0.5mm, the fan's flow rate at 2000Pa pressure is only 150L / min, which is too low to meet the product's flow requirements; when the gap width H is greater than 2mm, the fan's noise level at 1000Pa pressure exceeds 42dB, which is basically equivalent to the fan's noise without baffle 3, affecting the user experience; when the gap width H between the baffle 3 and the inner wall of volute 1 is 1.05mm, the fan's flow rate at 2000Pa pressure can reach 170L / min, and the noise level at 1000Pa pressure is 35dB, both of which meet the product's basic performance standards.

[0034] The fan provided in this application embodiment is a miniature fan used in ventilation therapy equipment (such as ventilators or high-flow humidified oxygen therapy devices), wherein the diameter of the impeller 2 is typically within 40-55 mm (e.g., 42 mm-46 mm) to provide the air volume and air pressure required by the ventilation therapy equipment. The inlet and outlet dimensions of the impeller 2 also affect the fan's flow rate. The inlet diameter of the impeller 2 (e.g., the diameter of the inner edge 202 of the inlet) is typically 10-20 mm, for example, 12-18 mm, or approximately 15-16 mm; the height F of the outlet 204 of the impeller 2 is typically set to 0.3-10 mm, for example, 1.5-5 mm, or approximately 2 mm.

[0035] Based on the impeller 2 size and the air volume requirements of the ventilation therapy equipment, the gap width H between the baffle 3 and the inner wall of the volute 1 can be maintained at 0.8mm-1.5mm (for example, about 1mm) to better eliminate the influence of the baffle 3 on the fan flow and / or air pressure.

[0036] In particular, the inventors of this application have discovered that, in addition to the influence of the impeller 2's own dimensions (e.g., the diameter, height, or outlet area of ​​the impeller 2), the size of the gap between the impeller 2 and the volute 1, and the relationship between this gap size and the gap size between the baffle 3 and the inner wall of the volute 1, also affect the fan's noise and flow rate. When the gap size between the impeller 2 and the volute 1 is too large, the airflow delivered from the outlet 204 of the impeller 2 is prone to generating turbulence in the space corresponding to this gap (i.e., the cavity formed by the impeller 2, baffle 3, and volute 1), leading to increased fan noise. When the gap size between the impeller 2 and the volute 1 is too small, the airflow delivered from the outlet 204 of the impeller 2 does not have sufficient buffer distance, resulting in higher noise. Furthermore, if the gap size between the impeller 2 and the volute 1 is too small, it may also lead to excessively high gas pressure in the space corresponding to this gap. Since the gas passage capacity of the gap between the baffle 3 and the volute 1 is limited, high-pressure gas may leak back to the low-pressure area near the air inlet of the impeller 2, affecting the fan's flow rate and / or pressure. Therefore, it is necessary to balance the dimensional relationship between the gap between the impeller 2 and the volute 1 and the gap between the baffle 3 and the inner wall of the volute 1.

[0037] In response, the inventors of this application have discovered that controlling the gap width E between the impeller 2 and the volute 1, and the gap width H between the baffle 3 and the inner wall of the volute 1, satisfies: 0.95H≤E≤8H; and / or, the gap area S1 between the impeller 2 and the volute 1, and the gap area S2 between the baffle 3 and the inner wall of the volute 1, satisfies: 0.95S2≤S1≤8S2, which can better balance the flow rate and noise requirements of the fan.

[0038] In some embodiments, the gap width E between the impeller 2 and the volute 1 can be approximately 1.5mm-6mm, for example, approximately 2mm-5.5mm. In some embodiments, the gap width E can be set to satisfy the condition that the diameter of the impeller 2 is 8-25 times the gap width E between the impeller 2 and the volute 1.

[0039] In some embodiments, the outer diameter of the fan is typically in the range of 50-70mm, for example, about 60mm, to be suitable for assembly in ventilation therapy equipment such as ventilators, and to meet the design requirements of the impeller 2 and the baffle 3 in the fan, as well as the design requirements of the gap between the two components and the volute 1.

[0040] In some embodiments, the air inlet channel 106 can be formed at the top of the volute 1, and the impeller 2 is located below the air inlet channel 106. The air inlet channel 106 can be used to deliver gas to the impeller 2. The air outlet channel 108 can be formed on the side of the volute 1. In some embodiments, the baffle 3 is located on the side of the air outlet channel 108 near the air inlet channel 106, thereby being located above the air outlet channel 108, so that the gas flowing out of the air outlet 204 first passes through the noise reduction channel 304 to reduce noise, and then flows out through the air outlet channel 108. The baffle 3 can divide the cavity 107 into two chambers. The chamber above the baffle 3 that houses the impeller 2 can serve as the air inlet chamber, and the chamber below the baffle 3 that is directly connected to the air outlet channel 108 can serve as the air outlet chamber.

[0041] In some implementations, see Figures 1-7 As shown, the fan provided in this application includes a drive device, which is connected to the mounting portion 206 of the impeller 2 to drive the impeller 2 to rotate. A baffle 3 is located on the side of the impeller 2 away from the inlet channel 106 and not lower than the top edge of the outlet channel 108. The baffle 3 is connected to the drive device, and the baffle 3 is spaced from the inner wall of the volute 1 to form an annular noise reduction channel 304. See also... Figure 1 and Figure 5 As shown, the radial spacing of the noise reduction channel 304 (i.e., the gap width H between the partition 3 and the inner wall of the volute 1) is smaller than the radial spacing between the first outer edge 203 of the impeller 2 and the inner wall of the volute 1. According to the fan of this application, when gas flows from the cavity 107 through the noise reduction channel 304, the area of ​​the flow cross section decreases, which increases the resistance to the gas, thereby reducing the gas velocity and changing the gas flow state from turbulent to laminar flow, thus reducing the turbulent noise of the gas.

[0042] In some implementations, the driving device includes, but is not limited to, a motor 5, a speed reducer, etc. For example, in conjunction with... Figures 1-3 and Figure 7 As shown, the driving device includes a motor 5, and the output shaft of the motor 5 is connected to the mounting portion 206 of the impeller 2 to drive the impeller 2 to rotate. Furthermore, to prevent the impeller 2 from axially moving relative to the output shaft of the motor 5 during rotation, the output shaft of the motor 5 is interference-fitted with the mounting portion 206.

[0043] In some embodiments, the partition 3 may be disposed on the top of the motor housing, and the output shaft of the motor 5 passes through the partition 3 and is connected to the mounting portion 206 of the impeller 2 for transmission.

[0044] In some implementations, combined Figure 1 and Figure 8 As shown, the partition 3 is an annular plate, which is sleeved on the outer wall of the motor 5. The second outer edge 302 of the partition 3 and the inner wall of the volute form an annular noise reduction channel 304.

[0045] In some implementations, combined Figure 4 and Figure 5 As shown, the flow area S2 of the noise reduction channel 304 and the flow area S3 of the outlet 204 of the impeller 2 satisfy the condition: 1.5S3≤S2≤2.5S3. It can be understood that the airflow generated by the rotation of the impeller 2 flows out through the outlet 204; therefore, the total area (outflow area) of all outlets 204 of the impeller 2 affects the outlet flow rate and efficiency of the impeller 2. When the ratio of the flow area S2 of the noise reduction channel 304 to the flow area S3 of the outlet 204 of the impeller 2 is S2<1.5S3, the flow resistance of the gas flowing through the noise reduction channel 304 is too high, causing the fan to be unable to output a reasonable gas flow rate. When the ratio of the flow area S2 of the noise reduction channel 304 to the flow area S3 of the outlet 204 of the impeller 2 is S2>2.5S3, the noise reduction channel 304 cannot effectively rectify the airflow, and the airflow still has significant noise. Therefore, the ratio of the flow area S2 of the noise reduction channel 304 to the flow area S3 of the air outlet 204 of the impeller 2 is 1.5S3≤S2≤2.5S3, which can achieve a good noise reduction effect while ensuring that the fan outputs a reasonable gas flow rate.

[0046] Combination Figure 1 , Figures 4-8 As shown, the projected area of ​​the annular noise reduction channel 304 on the plane where the baffle 3 is located is the flow area S2 of the annular noise reduction channel 304 (i.e., the gap area between the baffle 3 and the inner wall of the volute 1). Multiple blades are arranged inside the impeller 2 to form multiple air ducts, and the outlet of the air duct is formed as the air outlet 204, i.e., see [reference] Figure 7 As shown, a plurality of air outlets 204 are formed along the first outer edge 203 of the impeller 2, and the flow area S3 of the air outlets 204 is the sum of the flow areas of the plurality of air outlets 204. In some embodiments, the flow area of ​​a single air outlet 204 is calculated by multiplying the height F of the air outlet 204 by the distance between the two blades at the air duct outlet, or, ignoring the blade thickness, by multiplying the height F of the air outlet 204 by the outer circumference length of the impeller 2.

[0047] In some implementations, see Figure 1 As shown, the inner wall of the volute 1 near the air outlet 204 of the impeller 2 is formed as a curved surface to guide the gas flowing out of the air outlet 204 downwards into the noise reduction channel 304, thereby reducing the backflow of gas from the fifth gap to the vicinity of the air inlet of the impeller 2. The gap between the impeller 2 and the volute 1 can be considered as the gap between the outer edge of the impeller 2 away from the air inlet channel 106 and the volute 1. In some embodiments, the inner diameter of the portion of the volute 1 corresponding to the outer edge of the impeller 2 away from the air inlet channel 106 is substantially the same as the inner diameter of the portion of the volute 1 corresponding to the baffle 3.

[0048] In some implementations, combined Figure 1 , Figures 5-8 As shown, the second outer edge 302 of the baffle 3 is closer to the inner wall of the volute 1 than the first outer edge 203 of the impeller 2. The radial spacing H of the noise reduction channel 304 refers to the distance between the second outer edge 302 of the baffle 3 and the inner wall of the volute. For example, the volute 1 includes an upper volute 6 and a lower volute 4 that can be assembled together. The radial spacing H of the noise reduction channel 304 refers to the distance between the second outer edge 302 of the baffle 3 and the inner wall 104 of the upper volute 6. The gap width E between the impeller 2 and the volute 1 refers to the distance between the first outer edge 203 of the impeller 2 and the inner wall 104 of the upper volute. The radial spacing H between the second outer edge 302 of the baffle 3 and the inner wall 104 of the upper volute and the radial spacing E between the first outer edge 203 of the impeller 2 and the inner wall 104 of the upper volute satisfy: 0.95H ≤ E ≤ 8H. By adjusting the radial distance H between the second outer edge 302 of the partition 3 and the inner wall 104 of the upper volute, the fan performance can balance the flow demand and noise reduction demand.

[0049] In some implementations, combined Figure 1 , Figures 5-8 As shown, the baffle 3 is spaced apart from the impeller 2 and located below the impeller 2. A third gap exists between the upper surface 301 of the baffle 3 and the lower surface 205 of the impeller, with an axial spacing G of 0.3-5 mm. It is understood that when the axial spacing G of the third gap is greater than 5 mm, the airflow from the outlet 204 may enter the gap between the baffle 3 and the impeller 2, generating turbulence and increasing airflow noise. When the axial spacing G of the third gap is less than 0.3 mm, the impeller 2 is prone to interference with the baffle 3 during rotation, affecting the normal operation of the impeller 2. Therefore, in the fan of this application, by controlling the axial spacing G of the third gap, the flow state of the gas between the impeller 2 and the baffle 3 can be controlled, thereby controlling the noise level generated by the gas. Setting the axial spacing G of the third gap to 0.3-5 mm ensures that the impeller 2 and the baffle 3 do not interfere with each other while reducing gas noise.

[0050] In some implementations, combined Figure 1 , Figures 5-8 As shown, the baffle 3 is positioned above the air outlet duct 108, allowing the gas flowing from the air outlet 204 to first pass through the noise reduction channel 304 to reduce noise before flowing out through the air outlet 108. Preferably, the baffle 3 has an upper upper surface 301, a second outer edge 302, and a lower surface 303. A fourth gap exists between the upper upper surface 301 and the top edge of the air outlet duct 108, i.e., the upper wall surface 103 of the air outlet duct, and the axial distance A of the fourth gap does not exceed 10 mm. In some embodiments, combined with... Figure 4 and Figure 6 As shown, the air outlet duct 108 is a cylindrical channel, the upper wall 103 of the air outlet duct is curved, and the inlet of the air outlet duct 108 is circular. The axial distance A of the fourth gap between the upper surface 301 of the baffle plate 3 and the upper wall 103 of the air outlet duct 108 refers to the minimum distance from the upper surface 301 of the baffle plate 3 to the circular inlet. It can be understood that forming a fourth gap between the upper surface 301 of the baffle plate 3 and the upper wall 103 of the air outlet duct ensures that the gas flowing out of the air outlet 204 first flows through the noise reduction channel 304 and then flows into the air outlet duct 108, thereby achieving noise reduction. In addition, controlling the axial distance A of the fourth gap to not exceed 10mm can avoid increasing the overall size of the fan, increasing production costs, and reducing the convenience of using the fan.

[0051] In some implementations, combined Figure 4 and Figure 7 As shown, the height F of the outlet 204 of impeller 2 is set to 0.3-10mm. Specifically, when the height F of outlet 204 is less than 0.3mm, the gas flow rate from outlet 204 is too small. To meet the output gas flow rate of the fan, motor 5 needs to increase its speed, resulting in greater noise. When the height F of outlet 204 is greater than 10mm, it may lead to an increase in the overall size of the fan, increasing production costs and reducing the ease of use of the fan. Therefore, by controlling the height F of outlet 204, the fan speed and the output gas flow rate can be controlled. Setting the height F of outlet 204 of impeller 2 to 0.3-10mm can ensure that the output gas flow rate of the fan meets the requirements for normal operation, while keeping the fan speed within a reasonable range to avoid excessive noise and also to avoid an increase in the overall size of the fan.

[0052] In some embodiments, the outlet end face 101 of the air inlet channel 106 is higher than the inlet end face 201 of the impeller 2, and the outlet end face 101 and the inlet end face 201 have a first gap along the axial direction.

[0053] In the fan provided in this application, the outlet end face 101 of the air inlet channel 106 is higher than the inlet end face 201 of the impeller 2. That is, there is a first axial gap between the outlet end face 101 of the air inlet channel 106 and the inlet end face 201 of the impeller 2. Therefore, the outlet end face 101 does not need to extend into the impeller 2, for example, it does not need to extend into the inlet end face 201 of the impeller 2, thereby reducing the manufacturing and processing difficulty of the volute. Specifically, when the fan is working, the impeller 2 is rotating. In order to avoid the part of the air inlet channel 106 extending into the inlet end face 201 of the impeller 2 from interfering with the rotation of the impeller 2, the air inlet channel 106 and the air inlet of the impeller 2 must be coaxially assembled, and the wall thickness of the outlet end face 101 must be kept uniform so that the air inlet of the impeller 2 and the outlet end face 101 maintain a constant radial distance when the impeller 2 is rotating. This results in higher processing precision for the volute, which in turn makes the processing of the volute more difficult. In this application, there is a first gap along the axial direction between the outlet end face 101 of the air inlet channel 106 and the inlet end face 201 of the impeller 2, which can reduce the manufacturing and processing difficulty of the volute.

[0054] In some implementations, combined Figures 1-7 As shown, the axial distance B of the first gap between the outlet end face 101 of the air inlet channel 106 and the inlet end face 201 of the impeller 2 does not exceed 10 mm. It is understood that the pressure at the air inlet of the impeller 2 is generally lower than the pressure at the air outlet 204. After the gas flows out of the air outlet 204, some gas may flow into the fifth gap between the impeller 2 and the inner wall of the volute, and then flow out from the outlet of this fifth gap. See [link to relevant documentation]. Figure 1 and Figure 5 As shown, the inlet of the fifth gap is close to the outlet 204 of the impeller 2, and the outlet of the fifth gap is close to the inlet channel 106 of the volute. Therefore, when the axial spacing B of the first gap is greater than 10 mm, the outlet of the fifth gap is relatively large, which easily leads to a large amount of gas flowing out from the outlet of the fifth gap. The outflowing gas collides with the gas flowing in from the inlet channel 106, generating noise. At the same time, the noise waves generated inside the volute will also escape through the outlet of the fifth gap, ultimately leading to increased noise and lower fan efficiency. Therefore, by controlling the axial spacing B of the first gap, the amount of gas overflowing from the fifth gap can be controlled, thereby controlling the noise generated by the fan and the fan efficiency. For example, the axial spacing B of the first gap is set to 0.8 mm, achieving a better noise reduction effect and higher fan efficiency.

[0055] In some implementations, see Figure 1 and Figure 5 As shown, the outer edge 102 of the outlet end face 101 of the air inlet channel 106 is located inside the inlet end face 201, and the outer edge 102 of the outlet and the inner edge 202 of the inlet end face 201 have a second gap in the radial direction. That is to say, combined with Figure 1-3 as well as Figures 5-7 As shown, along the axial extension direction of the fan, the projections of the outer edge 102 of the outlet and the inner edge 202 of the inlet are circular, and the projection of the outer edge 102 of the outlet is located inside the projection of the inner edge 202 of the inlet. For example, the projections of the outer edge 102 of the outlet and the inner edge 202 of the inlet are two concentric circles, and a second gap is formed between the two concentric circles.

[0056] In some embodiments, the radial spacing C of the second gap does not exceed 5 mm. It is understood that when the radial spacing C of the second gap is greater than 5 mm, the outlet of the fifth gap is larger, which easily leads to a larger amount of gas flowing out from the outlet of the fifth gap. The outflowing gas collides with the gas flowing in from the air inlet channel 106, generating noise. Simultaneously, the noise waves generated inside the volute also escape through the outlet of the fifth gap, ultimately increasing the noise level and reducing the fan's operating efficiency. Therefore, by controlling the radial spacing C of the second gap, the amount of gas overflowing from the fifth gap can be controlled, thereby controlling the noise generated by the fan and its operating efficiency. For example, the radial spacing C of the second gap is set to 0.8 mm, achieving a better noise reduction effect and higher fan operating efficiency.

[0057] In some implementations, such as Figure 1 and Figure 5 As shown, the impeller 2 has a double-layer structure, including an upper cover plate near the air inlet channel 106, a lower cover plate near the partition 3, and blades located between the upper and lower cover plates. The first gap and the second gap between the air inlet channel 106 and the impeller 2 refer to the distance between the air inlet channel 106 and the upper cover plate of the impeller 2.

[0058] In some implementations, see Figure 1 and Figure 5 As shown, the inner wall of the volute has a bent structure near the inlet end face 201 of the impeller 2. Part of this bent structure forms the outer wall of the air inlet channel 106. The inlet end face 201 is located below this bent structure. When the gas flows out along the fifth gap, it is blocked by the outer wall of the air inlet channel 106 at the outlet near the fifth gap and flows downward again into the impeller 2, thereby reducing gas leakage and further reducing noise.

[0059] In some implementations, see Figures 1-7As shown, the air inlet channel 106 has a guide structure near the cavity 107. This guide structure is configured to deliver gas to the impeller 2 at a preset angle D, reducing the impact of the airflow on the mounting portion 206 of the impeller 2. When gas enters the impeller 2, it impacts the mounting portion 206. By adjusting the delivery angle of at least part of the gas through the guide structure, the impact of the gas on the mounting portion 206 can be reduced, thereby reducing the aerodynamic noise generated by the impact on the mounting portion 206 and the energy loss caused by the impact.

[0060] According to the fan provided in this application, the air inlet channel 106, the cavity 107, and the air outlet channel 108 are connected sequentially along the gas flow direction. The air inlet channel 106 has a guide structure that is close to the cavity 107. The angle at which the air inlet channel 106 delivers gas to the impeller 2 can be adjusted by the guide structure, thereby delivering the gas to the impeller 2 at a preset angle D, thereby reducing the noise and energy loss generated by the gas impact on the mounting part 206, and thus reducing the working efficiency of the fan.

[0061] In some embodiments, the guide structure may include a guide sleeve disposed in the air inlet channel 106 and close to the cavity 107. The angle between the inner wall surface of the guide sleeve and the central axis of the guide sleeve is a preset angle. After the gas flows into the air inlet channel 106 and passes through the guide sleeve, it flows into the impeller 2 at a preset angle D, thereby reducing the impact of the gas on the mounting part 206.

[0062] In some implementations, combined Figure 1 and Figure 6 As shown, the angle between the air inlet inner wall surface 105 of the air inlet channel 106, which is at least close to the cavity 107, and the central axis of the air inlet channel 106 is formed as a preset angle to form a guide structure. By forming a guide structure through the air inlet inner wall surface 105, the structure of the fan casing can be simplified and the production cost can be reduced.

[0063] In some implementations, see Figure 1 and Figure 5 As shown, the guide structure can be formed as a tapering channel, that is, the diameter of the gas channel formed in the guide structure gradually decreases along the gas flow direction.

[0064] In one implementation, see Figure 1 and Figure 5 As shown, the air inlet inner wall surface 105 is formed as a guide structure, and the inclination degree of the air inlet inner wall surface 105 remains unchanged, that is, in Figure 1 and Figure 5 In the cross-sectional view shown, the outline of the air inlet inner wall 105 is a straight line. In another embodiment, the direction from the inlet to the outlet of the air inlet channel 106, i.e. Figure 1From top to bottom, the inclination of the inner wall 105 of the air inlet gradually increases, forming a rounded corner structure at the top of the air inlet channel 106.

[0065] The guide structure delivers gas to the impeller 2 at a preset angle D. The preset angle D can be adjusted according to the actual situation. In some embodiments, the preset angle D is set to no more than 45° to reduce the impact of the gas flowing into the impeller 2 on the mounting part 206.

[0066] Gas is delivered to the impeller 2 through the inlet channel 106, and a preset angle D is formed between the inlet inner wall surface 105 and the central axis of the inlet channel 106. According to the Coanda effect, when gas passes through the inlet channel 106, it tends to flow along or close to the inlet inner wall surface 105. Therefore, by adjusting the preset angle D, the angle at which the gas is delivered from the inlet channel 106 to the impeller 2 can be adjusted. In the above embodiment, the preset angle D is set to no more than 45° to reduce the impact of the gas flowing into the impeller 2 on the mounting portion 206. In some embodiments, the preset angle D is configured to allow the gas to avoid the mounting portion 206 of the impeller 2, thereby further reducing noise and energy loss. It is understandable that after the gas flows into the air inlet channel 106, most of the gas flows along or near the inner wall surface 105 of the air inlet. Simultaneously, when the fan is operating, the impeller 2 rotates, and the air duct formed by the blades of the impeller 2 generates suction on the gas. Therefore, the gas flowing into the impeller 2 will flow towards the air ducts on both sides of the mounting portion 206. By controlling the preset angle D, the gas can avoid the mounting portion 206, further reducing noise and energy loss. In some embodiments, the gas flow velocity is lower, and / or the gas flows into the air inlet channel 106 from the inlet side, making it easier for the gas to flow along the inner wall surface 105 of the air inlet, thus facilitating the gas delivered to the impeller 2 to avoid the mounting portion 206.

[0067] In the fan of this application, any of the above-mentioned preferred size parameters can be used to achieve noise reduction of the fan. Alternatively, several or all of the above-mentioned preferred size parameters can be combined to achieve a better noise reduction effect.

[0068] In addition, this application also provides a ventilation therapy device, including the aforementioned fan.

[0069] The preferred embodiments of this application have been described in detail above with reference to the accompanying drawings; however, this application is not limited thereto. Within the scope of the technical concept of this application, various simple modifications can be made to the technical solution of this application, including the combination of various specific technical features in any suitable manner. To avoid unnecessary repetition, this application will not describe the various possible combinations separately. However, these simple modifications and combinations should also be considered as the content disclosed in this application and are all within the protection scope of this application.

Claims

1. A fan, characterized in that, The device includes a volute (1), an impeller (2), and a baffle (3). The volute has an air inlet channel (106), a cavity (107), and an air outlet channel (108). The air inlet channel (106) and the air outlet channel (108) are connected via the cavity (107). The impeller (2) and the baffle (3) are respectively installed in the cavity (107) and spaced apart from the inner wall of the volute (1). The baffle (3) is located on the side of the impeller (2) away from the air inlet channel (106). Wherein, the gap width E between the impeller (2) and the volute (1), and the gap width H between the partition plate (3) and the inner wall of the volute (1) satisfy: 0.95H≤E≤8H; and / or, the gap area S1 between the impeller (2) and the volute (1), and the gap area S2 between the partition plate (3) and the inner wall of the volute (1) satisfy: 0.95S2≤S1≤8S2.

2. The fan according to claim 1, characterized in that, The gap width E between the impeller (2) and the volute (1), and the gap width H between the partition plate (3) and the inner wall of the volute (1) satisfy: H<E≤6H; and / or, the gap area S1 between the impeller (2) and the volute (1), and the gap area S2 between the partition plate (3) and the inner wall of the volute (1) satisfy: S2<S1≤6S2.

3. The fan according to claim 1 or 2, characterized in that, The gap width E between the impeller (2) and the volute (1) is set to 1.5mm-6mm; and / or, The gap width H between the partition (3) and the inner wall of the volute (1) is set to 0.5-2mm.

4. The fan according to claim 1, characterized in that, The gap area S2 between the partition (3) and the inner wall of the volute (1) satisfies the following condition with the outflow area S3 of the air outlet (204) of the impeller (2): 1.5S3≤S2≤2.5S3.

5. The fan according to claim 1, characterized in that, The partition (3) and the impeller (2) are spaced apart along the axial direction of the volute (1), and the axial distance G between the surfaces of the partition (3) and the impeller (2) that are arranged opposite to each other is set to 0.3-5mm.

6. The fan according to claim 1, characterized in that, The partition (3) is located on the side of the air outlet channel (108) near the air inlet channel (106).

7. The fan according to claim 6, characterized in that, The axial distance A between the surface of the partition (3) away from the air outlet channel (108) and the top edge of the air outlet channel (108) near the air inlet channel (106) does not exceed 10 mm.

8. The fan according to claim 1, characterized in that, The outlet end face (101) of the air inlet channel (106) is higher than the inlet end face (201) of the impeller (2), and has a first axial gap with the inlet end face (201) of the impeller (2); and / or, The outer edge (102) of the outlet end face (101) of the air inlet channel (106) is located inside the inlet end face (201) and has a second gap radially with the inner edge (202) of the inlet end face (201).

9. The fan according to claim 8, characterized in that, The axial spacing B of the first gap does not exceed 10 mm; and / or, The radial spacing C of the second gap does not exceed 5 mm.

10. The fan according to claim 1, characterized in that, The air inlet channel (106) is formed as a tapering channel in the direction close to the impeller (2), and the air inlet inner wall surface (105) of the air inlet channel (106) at least close to the cavity (107) is inclined outward relative to the central axis of the air inlet channel (106) to form a guide structure.

11. The fan according to claim 10, characterized in that, The angle between the inner wall surface (105) of the air inlet channel (106) and the central axis of the air inlet channel (106) shall not exceed 45°.

12. The fan according to claim 1, characterized in that, The fan meets at least one of the following conditions: The diameter of the impeller (2) is set to 40-55 mm; The diameter of the impeller (2) is set to be 8-25 times the gap width E between the impeller (2) and the volute (1); The height F of the air outlet (204) of the impeller (2) is set to 0.3-10mm; The inlet diameter of the impeller (2) is set to 10-20 mm; The outer diameter of the fan is set to 50-70mm.

13. A ventilation therapy device, characterized in that, Includes the wind turbine as described in any one of claims 1-12.

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