Fluid pump

Abstract

This application discloses a fluid pump, including a pump casing and an impeller. The pump casing has a receiving cavity, a first port, and a second port, both of which communicate with the receiving cavity. The impeller includes a connecting component and multiple blades. The connecting component is rotatably disposed within the receiving cavity. The multiple blades are radially connected to the connecting component around its rotation axis, and a flow guide channel is formed between adjacent blades. The flow guide channel has an inlet located near the rotation axis and an outlet located away from the rotation axis. The inlet communicates with the first port, and the outlet communicates with the second port through the receiving cavity. Along the direction away from the rotation axis, the blades include at least one arcuate section and a straight section, with the straight section located at the tail of the blade. This application solves the problem of poor noise reduction in existing fluid pumps.

Description

Technical Field

[0001] This application relates to the field of pump technology, and more specifically, to a fluid pump. Background Technology

[0002] Fluid pumps serve as the power source for the circulation systems of household appliances such as water heaters and central air conditioning systems, and are also a major source of noise in these systems. In related technologies, sound-absorbing and sound-insulating components are typically installed on the fluid pump, or vibration-damping components are added to the pump's base, in order to reduce noise. However, both of these solutions require additional noise-reducing components on the fluid pump. After a period of use, the noise-reducing effect of the fluid pump will significantly weaken as the noise-reducing components age, and the problem of poor noise reduction still exists. Utility Model Content

[0003] The main objective of this application is to provide a fluid pump to solve the problem of poor noise reduction performance of fluid pumps in the prior art.

[0004] According to one aspect of this application, a fluid pump is provided, comprising: A pump housing, wherein the pump housing is provided with a receiving cavity, a first port and a second port, both the first port and the second port being connected to the receiving cavity; An impeller includes a connecting component and multiple blades. The connecting component is rotatably disposed within the receiving cavity. The multiple blades are radially connected to the connecting component around its rotation axis, and a flow channel is formed between adjacent blades. The flow channel has an inlet located near the rotation axis and an outlet located away from the rotation axis. The inlet communicates with a first port, and the outlet communicates with a second port through the receiving cavity. The blade includes at least one arcuate segment and a straight segment along a direction opposite to the axis of rotation, with the straight segment located at the tail of the blade.

[0005] Furthermore, along the direction away from the axis of rotation, the arc length of the arc segment is L1, and the length of the straight segment is L2, wherein L1 and L2 satisfy the relationship: 1 / 6≤L2 / (L1+L2)≤1 / 4.

[0006] Furthermore, the width of the blade gradually decreases along the direction opposite to the axis of rotation.

[0007] Furthermore, the straight section extends to the outer edge of the connecting member in a direction opposite to the axis of rotation.

[0008] Furthermore, the straight line perpendicular to the axis of rotation and passing through the end of the arc segment near the axis of rotation is the first straight line, and the straight line perpendicular to the axis of rotation and passing through the end of the straight segment away from the axis of rotation is the second straight line. The angle formed by the intersection of the first straight line and the second straight line is α, and α satisfies the relationship: 90°≤a≤120°.

[0009] Furthermore, the connecting component includes a first circle, and the ends of each arc segment near the axis of rotation are all on the outer edge contour of the first circle. The tangent of the blade through the end of the arc segment near the axis of rotation is a third straight line, and the tangent of the first circle through the end of the arc segment near the axis of rotation is a fourth straight line. The included angle formed by the intersection of the third straight line and the fourth straight line is b1, and b1 satisfies the relationship: 20°≤b1≤35°.

[0010] Furthermore, the connecting component includes a second circle, and the ends of each of the straight segments away from the axis of rotation are all on the outer edge contour of the second circle. The tangent of the blade through the end of the straight segment away from the axis of rotation is a fifth straight line, and the tangent of the second circle through the end of the straight segment away from the axis of rotation is a sixth straight line. The included angle formed by the intersection of the fifth straight line and the sixth straight line is b2, and b2 satisfies the relationship: 35°≤b2≤50°.

[0011] Furthermore, along the direction of the rotation axis, the connecting component includes a first annular cover plate and a second annular cover plate spaced apart. The axis of the first annular cover plate, the axis of the second annular cover plate, and the rotation axis coincide. The blade is connected between the first annular cover plate and the second annular cover plate. The inner ring wall of the first annular cover plate forms a first channel. The inlet of the guide channel is connected to the first port through the first channel.

[0012] Furthermore, the outer diameter of both the first annular cover plate and the second annular cover plate is d1, where 68mm≤d1≤74mm.

[0013] Furthermore, the side of the first annular cover plate closest to the second annular cover plate is designated as the first side, and the side of the second annular cover plate closest to the first annular cover plate is designated as the second side. At least a portion of the outer ring of the first side closest to the first annular cover plate and at least a portion of the outer ring of the second side closest to the second annular cover plate are parallel to each other and perpendicular to the axis of rotation, respectively.

[0014] Furthermore, the diameter of the inner ring of the first annular cover plate is d2, where 20mm ≤ d2 ≤ 24mm.

[0015] Furthermore, the side of the second annular cover plate closest to the first annular cover plate is the second side, and at least a portion of the inner ring of the second side near the second annular cover plate forms an annular planar region, which is perpendicular to the axis of rotation.

[0016] Furthermore, along the axial direction of the rotation axis, the minimum distance between the outer edge of the first annular cover plate and the outer edge of the second annular cover plate is c1, where 2mm ≤ c1 ≤ 3mm.

[0017] Furthermore, the maximum width of the blade is c2, where 9mm ≤ c2 ≤ 10mm.

[0018] Furthermore, the end of the arc-shaped segment near the axis of rotation extends to the inner ring wall of the first annular cover plate.

[0019] Furthermore, along the radial direction of the annular plane region, the distance from the outer ring to the inner ring of the annular plane region is c3, and c3 satisfies the relationship: 8.2mm < c3 < 8.4mm.

[0020] Furthermore, the fluid pump also includes: A first conveying channel is connected to the first port, and the end of the first conveying channel away from the first port has a liquid inlet. The second conveying channel is connected to the second port.

[0021] Furthermore, along the direction of the rotation axis, the distance between the geometric center of the liquid inlet and the geometric center of the first port is f1, where 0.5mm≤f1≤1mm.

[0022] Furthermore, the first conveying channel is at least partially spaced from the plane containing the first port, along the axial direction of the rotation axis. The plane containing the liquid inlet is perpendicular to the rotation axis. The first conveying channel extends at least partially away from the rotation axis and has a predetermined gap with the plane containing the liquid inlet. The maximum value of the predetermined gap is f2, where 4mm ≤ f2 ≤ 5.5mm. Furthermore, the maximum distance between the plane on the side of the first conveying channel away from the liquid inlet and the plane on which the liquid inlet is located is f3, where 24mm≤f3≤26mm.

[0023] Furthermore, the geometric center of the second port is located in the plane where the liquid inlet is located, and along the direction of the rotation axis, the distance between the geometric center of the second port and the geometric center of the accommodating cavity is f4, 10mm≤f4≤11mm.

[0024] Furthermore, the pump casing includes a tongue having a starting end and a ending end, the ending end being connected to the inner wall surface of the accommodating cavity. Along the direction opposite to the rotation axis, the distance between the outer edge of the impeller and the inner wall surface of the accommodating cavity is w, and w gradually increases along the direction from the starting end to the ending end of the tongue.

[0025] Furthermore, the tongue has a tongue placement angle β, where 35°≤β≤40°.

[0026] In this application, by configuring the blades with at least one arc-shaped segment and a straight segment, with the straight segment located at the blade tail, the straight segment adjusts the flow direction of the fluid after it accelerates through the arc-shaped segment, effectively preventing severe turbulence caused by chaotic velocity direction at the outlet of the guide channel. Simultaneously, the straight segment allows the fluid to enter the pump casing's receiving cavity more smoothly and then flow out from the second port, reducing backflow and impact within the receiving cavity, thus lowering flow noise. This application reduces noise generation at its source by improving the noise generated during fluid flow, eliminating the need for external noise reduction equipment and achieving better noise reduction results. Attached Figure Description

[0027] The accompanying drawings, which are included to provide a further understanding of this application and form part of this application, illustrate exemplary embodiments and are used to explain this application, but do not constitute an undue limitation of this application. In the drawings: Figure 1 This is a schematic diagram of the structure of the fluid pump disclosed in this application; Figure 2 This is a schematic diagram of the bottom structure of the fluid pump disclosed in this application; Figure 3 This is a cross-sectional view of the fluid pump disclosed in this application; Figure 4 A schematic diagram of the impeller disclosed in this application (I); Figure 5 This is a schematic diagram (II) of the impeller structure disclosed in this application; Figure 6 This is a schematic diagram of the internal structure of the impeller disclosed in this application; Figure 7 This is a top view of the interior of the impeller disclosed in this application; Figure 8 This is a cross-sectional view of the impeller disclosed in this application; Figure 9 The simulation iteration diagram of the turbulent energy disclosed in this application is shown. Figure 10 This is a cross-sectional view of the pump casing disclosed in this application; Figure 11 This is a sectional view of the pump casing in the first section; Figure 12 This is a sectional view of the pump casing at the second section. Figure 13 This is a sectional view of the pump casing at the third section. Figure 14 This is a sectional view of the pump casing at the fourth section. Figure 15 This is a sectional view of the pump casing at the fifth section; Figure 16 This is a sectional view of the pump casing at the sixth section; Figure 17 This is a sectional view of the pump casing at the seventh section; Figure 18 This is a sectional view of the pump casing at the eighth section.

[0028] The above figures include the following reference numerals: 10. Pump casing; 20. Impeller; 11. Receptacle; 12. First port; 13. Second port; 21. Connecting component; 211. First annular cover plate; 212. Second annular cover plate; 213. First side; 214. Second side; 215. Annular planar area; 22. Blade; 221. Arc-shaped section; 222. Straight section; 23. Guide channel; 24. Inlet; 25. Outlet; 26. First channel; 30. First conveying channel; 31. Liquid inlet; 40. Second conveying channel; 50. Tongue. Detailed Implementation

[0029] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. This application will now be described in detail with reference to the accompanying drawings and embodiments.

[0030] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0031] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this application. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0032] like Figures 1 to 18 As shown, this application provides a fluid pump.

[0033] Specifically, the fluid pump includes a pump casing 10 and an impeller 20. The pump casing 10 has a receiving cavity 11, a first port 12, and a second port 13. Both the first port 12 and the second port 13 communicate with the receiving cavity 11. The impeller 20 includes a connecting component 21 and multiple blades 22. The connecting component 21 is rotatably disposed within the receiving cavity 11. The multiple blades 22 are radially connected to the connecting component 21 around its rotation axis P7, and a flow guide channel 23 is formed between adjacent blades 22. The flow guide channel 23 has an inlet 24 located near the rotation axis P7 and an outlet 25 located away from the rotation axis P7. The inlet 24 of the flow guide channel 23 communicates with the first port 12, and the outlet 25 of the flow guide channel 23 communicates with the second port 13 through the receiving cavity 11. The flow guide channel 23 is located in the direction away from the rotation axis P7 (e.g., along the direction away from the rotation axis P7). Figure 3 (in the direction indicated by the middle arrow X), the blade 22 includes at least one arcuate segment 221 and a straight segment 222, the straight segment 222 being disposed at the tail of the blade 22.

[0034] In this embodiment, the inlet 24 of the guide channel 23 is close to the rotation axis P7. After the fluid enters the guide channel 23 from the first port 12 and the inlet 24, it first contacts the arc-shaped section 221 of the blade 22. The arc-shaped section 221 is more in line with the inertial flow trajectory of the fluid, which can reduce the formation of fluid eddies and impacts at the inlet 24 of the blade 22. It allows the fluid to smoothly transition along the curved surface of the arc-shaped section 221, reducing the turbulence intensity at the inflow and reducing the generation of disturbance noise from the source. After the fluid accelerates through the arc-shaped section 221, the straight section 222 can adjust the flow direction of the fluid, effectively preventing the fluid from generating severe turbulence at the outlet 25 of the guide channel 23 due to chaotic velocity direction. At the same time, the straight section 222 allows the fluid to enter the receiving cavity 11 of the pump casing 10 more smoothly and then flow out from the second port 13, reducing the backflow and impact of the fluid in the receiving cavity 11, which can reduce flow noise. This embodiment achieves noise reduction by optimizing the structure of the blade 22 itself, eliminating the need for additional noise reduction components and reducing the number of pump body parts. The arc-shaped segment 221 can be one or more. When there is only one arc-shaped segment 221, it is connected to the straight segment 222. When there are multiple arc-shaped segments 221, they are connected sequentially, with the last arc-shaped segment 221 connected to the straight segment 222.

[0035] Furthermore, the curved surface of the arc-shaped section 221 conforms to the principles of fluid dynamics, reducing energy loss (such as impact loss and friction loss) at the inlet 24 and ensuring smooth fluid intake. The straight section 222 allows the fluid to flow out at a more optimal speed and direction, reducing energy dissipation within the accommodating cavity 11 and ensuring that the core performance indicators of the fluid pump, such as flow rate and head, are not affected, achieving a balance between noise reduction and efficient delivery.

[0036] like Figure 7As shown, further, along the direction away from the rotation axis P7, the arc length of the arc segment 221 is L1, and the length of the straight segment 222 is L2, where L1 and L2 satisfy the relationship: 1 / 6≤L2 / (L1+L2)≤1 / 4. This embodiment can accurately balance the functional synergy between the arc segment 221 and the straight segment 222, ensuring that the arc segment 221 has a sufficient arc length to fully conform to the fluid's inertial flow trajectory, guiding the fluid smoothly into the guide channel 23, minimizing the impact disturbance and turbulence noise at the inlet 24, and avoiding the problem of unsmooth inflow caused by the arc segment 221 being too short. At the same time, through the straight segment 222 of a reasonable length, after the fluid is accelerated by the arc segment 221, the fluid flow direction is effectively regulated, preventing severe turbulence at the outlet 25 due to the chaotic fluid velocity direction. At the same time, it avoids the situation where the straight segment 222 is too long, increasing fluid friction loss, or too short, failing to stabilize the flow field. By optimizing noise generation at the source, fluid transport efficiency is further guaranteed. The inflow stability is not sacrificed due to insufficient proportion of the arc section 221, nor is the outflow stability affected by improper length of the straight section 222. This achieves a precise match between noise reduction effect, fluid dynamic performance and structural economy, allowing the blade 22 to continuously play a stable noise reduction and efficient transport role in long-term operation without relying on additional noise reduction components, further improving the reliability and practicality of the fluid pump. like Figure 6 As shown, furthermore, the width of the blade 22 gradually decreases along the direction away from the rotation axis P7. When fluid flows from the inlet 24 near the rotation axis P7 to the outlet 25, the gradually decreasing width of the blade 22 as the rotation radius increases reduces the frictional resistance of the fluid during flow, reduces energy loss, ensures the pump's delivery efficiency, and prevents a decrease in flow rate and head due to excessive resistance. In addition, the reduced width of the blade 22 lightens the overall weight of the blade 22, reduces the rotational load on the connecting component 21, and reduces vibration and noise caused by uneven mass distribution of the blade 22. Specifically, the blade 22 can be configured with at least seven blades.

[0037] Furthermore, along the direction opposite to the rotation axis P7, the straight section 222 extends to the outer edge of the connecting component 21. The regulating effect of the straight section 222 on the fluid extends to the outlet 25 of the guide channel 23. After being guided by the arc-shaped section 221, the fluid can smoothly transition to the outer edge of the connecting component 21 under the full constraint of the straight section 222, thereby effectively reducing the turbulent eddies and impacts of the fluid at the outlet 25, having a good noise reduction effect, and allowing the fluid to enter the receiving cavity 11 in a more stable state and flow to the second port 13.

[0038] like Figure 7As shown, further, the straight line perpendicular to the rotation axis P7 and passing through the end of the arc segment 221 near the rotation axis P7 is the first straight line P1, and the straight line perpendicular to the rotation axis P7 and passing through the end of the straight segment 222 away from the rotation axis P7 is the second straight line P2. The angle formed by the intersection of the first straight line P1 and the second straight line P2 is α, which satisfies the relationship: 90°≤a≤120°. α is the wrap angle of the blade 22. α can be set to one of 90°, 95°, 100°, 105°, 110°, 115°, or 120°. When α satisfies the relationship 90°≤a≤120°, the blade 22 can accurately match the accelerated flow trajectory of the fluid in the guide channel 23. When the arc segment 221 guides the fluid to be drawn in from near the rotation axis P7, it can provide sufficient buffer space for the fluid. When the straight section 222 receives the fluid flowing out of the curved section 221, it can reduce fluid turbulence and disturbance, reduce noise caused by turning impact at the source, and also ensure the acceleration efficiency of the fluid, ensuring stable fluid transport efficiency. When a < 90°, it will cause severe turning impact of the fluid at the junction of the curved section 221 and the straight section 222. When a > 120°, it is easy to cause waste of guide channel space and fluid velocity attenuation.

[0039] like Figure 7As shown, the connecting component 21 further includes a first circle O1. The ends of each arc segment 221 near the rotation axis P7 are all on the outer edge contour of the first circle O1. The tangent of the blade 22 through the end of the arc segment 221 near the rotation axis P7 is the third straight line P3, and the tangent of the first circle O1 through the end of the arc segment 221 near the rotation axis P7 is the fourth straight line P4. The included angle formed by the intersection of the third straight line P3 and the fourth straight line P4 is b1, which satisfies the relationship: 20°≤b1≤35°. The included angle b1 is the inlet angle of the blade 22. b1 can be set to one of 20°, 25°, 30°, 35°, etc. The included angle b1 allows the blade 22 to form a gentle contact angle with the direction of fluid movement, which can greatly reduce the impact loss of the fluid at the inlet 24, allow the fluid to smoothly transition along the curved surface of the arc segment 221, reduce the turbulence intensity, and further enhance the noise reduction effect at the source. If b1 < 20°, the fluid impacting the blade 22 will generate severe impact disturbance, easily causing high-frequency noise. If b1 > 35°, the inlet angle is too large, making it difficult for the fluid to smoothly adhere to the blade 22, easily forming an inlet vortex phenomenon, resulting in energy waste. Furthermore, the connecting component 21 includes a second circle O2. The ends of each straight section 222 away from the rotation axis P7 are all on the outer edge contour of the second circle O2. The tangent to the end of the straight section 222 away from the rotation axis P7 is the fifth straight line P5, and the tangent to the end of the second circle O2 away from the rotation axis P7 is the sixth straight line P6. The included angle formed by the intersection of the fifth straight line P5 and the sixth straight line P6 is b2, which satisfies the relationship: 35° ≤ b2 ≤ 50°. The included angle b2 is the outlet angle 25 of the blade 22. b2 can be set to one of 35°, 40°, 45°, or 50°. The outlet angle b2 at 25° precisely matches the flow characteristics of the fluid after acceleration via the arc section 221 and straightening via the straight section 222. This provides a reasonable outflow guide angle for the fluid, reducing kinetic energy loss at outlet 25 and allowing the fluid to enter the receiving cavity 11 more orderly and flow towards the second port 13, further reducing flow disturbance. If b2 < 35°, the fluid may be obstructed at outlet 25, causing backflow or impacting the inner wall of the receiving cavity 11, which can easily lead to low-frequency vibration noise. If b2 > 50°, the outlet angle at 25° is too large, causing the fluid outflow direction to be too dispersed, exacerbating fluid turbulence within the receiving cavity 11, and increasing turbulent noise.

[0040] like Figure 7 As shown, further, along the direction of the rotation axis P7 (such as...) Figure 3(In the direction indicated by the middle arrow Y), the connecting component 21 includes a first annular cover plate 211 and a second annular cover plate 212 spaced apart. The axis of the first annular cover plate 211, the axis of the second annular cover plate 212, and the rotation axis P7 coincide. The blade 22 is connected between the first annular cover plate 211 and the second annular cover plate 212. The inner annular wall of the first annular cover plate 211 forms a first channel 26, and the inlet 24 of the guide channel 23 communicates with the first port 12 through the first channel 26. The first annular cover plate 211 and the second annular cover plate 212 form the sidewall of the guide channel 23 between the blades 22. That is, the first annular cover plate 211, the second annular cover plate 212, and two adjacent blades 22 surround and form the guide channel 23. The guide channel 23 can limit the flow of fluid, ensuring that the fluid always flows in an orderly manner within the guide channel 23. Meanwhile, the first channel 26 formed on the inner ring wall of the first annular cover plate 211 can precisely connect the inlet 24 of the guide channel 23 and the first port 12, providing directional guidance for the fluid to enter the guide channel 23 from the first port 12, reducing the diffusion loss and disturbance of the fluid at the inlet 24. The axis of the first annular cover plate 211, the axis of the second annular cover plate 212, and the rotation axis P7 are coincident, which can ensure the coaxiality of the flow channel when the blade 22 rotates, avoid the flow field shift caused by eccentricity, reduce the generation of local eddies, and reduce vibration noise caused by uneven force.

[0041] like Figure 7 As shown, further, the outer diameter of both the first annular cover plate 211 and the second annular cover plate 212 is d1, where 68mm ≤ d1 ≤ 74mm. d1 can be set to one of the following: 68mm, 69mm, 70mm, 71mm, 72mm, 73mm, 74mm, etc. This fluid pump can be used in the circulation systems of household appliances such as water heaters and central air conditioning systems, and has the advantages of small size and easy installation. If d1 < 68mm, the effective working area of ​​the blades 22 is insufficient, which cannot meet the fluid delivery requirements of the household appliances. If d1 > 74mm, it will exceed the reserved space inside the household appliances, increasing the difficulty of assembly and even interfering with other components.

[0042] Furthermore, the side of the first annular cover plate 211 closest to the second annular cover plate 212 is designated as the first side 213. The side of the second annular cover plate 212 closest to the first annular cover plate 211 is designated as the second side 214. At least a portion of the outer ring of the first side 213 closest to the first annular cover plate 211 and at least a portion of the outer ring of the second side 214 closest to the second annular cover plate 212 are parallel to each other and perpendicular to the rotation axis P7, respectively. This arrangement restricts fluid deviation or diffusion in the radial direction of the guide channel 23, ensuring that the fluid always flows smoothly radially towards the receiving cavity 11, reducing flow field turbulence, and lowering impact noise and turbulence noise caused by fluid deviation against the inner wall of the pump casing 10. The outlet 25 side of the guide channel 23 is perpendicular to the rotation axis P7, allowing the first annular cover plate 211 and the second annular cover plate 212 to provide more uniform support for the blade 22. When the blade 22 rotates at high speed, it can balance the radial and axial impact forces of the fluid on the blade 22, reducing the risk of blade deformation, reducing the rotational load on the connecting component 21, and reducing vibration noise. like Figure 4 As shown, further, the diameter of the inner ring of the first annular cover plate 211 is d2, where 20mm ≤ d2 ≤ 24mm. d2 is the diameter at which the fluid flows into the impeller 20, and d2 can be set to one of 20mm, 21mm, 22mm, 23mm, or 24mm. This setting provides a suitable flow cross-section for the fluid to enter the guide channel 23 from the first port 12, ensuring that the fluid enters the guide channel 23 in a stable and uniform state, further reducing the disturbance noise at the inlet 24. If d2 < 20mm, the fluid velocity at the inlet 24 will be too high, turbulence will be aggravated, impact noise will be generated, and energy loss will be increased. If d2 > 24mm, the inlet 24 channel will be too wide, and the fluid diffusion will be severe, resulting in uneven fluid distribution at the inlet 24 of the guide channel 23, and some blades 22 will not be able to do sufficient work. In addition, the inner ring diameter of 20mm≤d2≤24mm meets the fluid input flow requirements of household appliance circulation systems such as water heaters and central air conditioning. It can meet the system's requirements for circulation power without increasing the overall volume of the pump body due to the excessively large inlet 24 channels.

[0043] like Figure 8 As shown, further, the side of the second annular cover plate 212 closest to the first annular cover plate 211 is the second side 214. At least a portion of the second side 214 near the inner ring of the second annular cover plate 212 forms an annular planar region 215, which is perpendicular to the rotation axis P7. This annular planar region 215 can form a first channel 26 with the inner ring of the first annular cover plate 211. When fluid enters the guide channel 23 from the first port 12 through the first channel 26, the annular planar region 215 can provide stable support and directional guidance for the fluid, preventing the generation of local eddies and ensuring that the fluid is distributed to the inlets 24 of each guide channel 23 in a more uniform and stable state, thereby minimizing the impact noise and energy loss at the inlets 24.

[0044] Wherein, along the radial direction of the annular plane region 215, the distance from the outer ring to the inner ring of the annular plane region 215 is c3, and c3 satisfies the relationship: 8.2mm < c3 < 8.4mm. c3 can be set to one of 8.2mm, 8.25mm, 8.3mm, 8.35mm, 8.4mm, etc.

[0045] like Figure 8 As shown, further, along the axial direction of the rotation axis P7, the minimum distance between the outer edges of the first annular cover plate 211 and the second annular cover plate 212 is c1, where 2mm ≤ c1 ≤ 3mm. c can also be considered as the width at the outlet 25 of the guide channel 23. c1 can be set to one of 2mm, 2.2mm, 2.4mm, 2.6mm, 2.8mm, 3mm, etc. If c1 < 2mm, the axial space of the guide channel 23 will be narrow, and the fluid flow will be obstructed, which will cause a sudden increase in local flow velocity, intensified turbulence noise, and increased frictional energy loss. If c1 > 3mm, the guide channel 23 will be too wide, and the fluid will diffuse along the axial direction, which will weaken the guiding effect of the blade 22 on the fluid, and some fluid will not be able to effectively obtain kinetic energy, reducing the conveying efficiency.

[0046] Furthermore, the maximum width of blade 22 is c2, where 9mm ≤ c2 ≤ 10mm. As the width of blade 22 gradually decreases, the maximum width of blade 22 is the width at its starting end, allowing the fluid to obtain sufficient space for kinetic energy conversion within the channel, ensuring stable head and flow performance of the fluid pump. c2 can be set to one of the following: 9mm, 9.1mm, 9.2mm, 9.3mm, 9.4mm, 9.5mm, 9.6mm, 9.7mm, 9.8mm, 9.9mm, or 10mm. If c2 < 9mm, the channel becomes too narrow, resulting in insufficient fluid flow and failing to meet the flow requirements of the household appliance circulation system. This can also easily lead to excessively high local flow velocities and increased turbulence noise. If c2 > 10mm, an excessively large c2 causes blade 22 to occupy too much space and compress adjacent guide channels 23, leading to turbulent flow and increased fluid friction losses.

[0047] Furthermore, the end of the arc-shaped segment 221 near the axis of rotation P7 extends to the inner ring wall of the first annular cover plate 211. After the fluid enters through the first channel 26 formed by the inner ring of the first annular cover plate 211, it can flow directly along the curved surface of the arc-shaped segment 221, avoiding the phenomenon of fluid stagnation at the inlet 24 due to the gap between the end of the arc-shaped segment 221 and the inner ring wall, reducing local eddies and impact noise, and enhancing the smooth flow state of the fluid at the inlet 24.

[0048] Furthermore, the fluid pump also includes a first delivery channel 30 and a second delivery channel 40. The first delivery channel 30 is connected to the first port 12, and the end of the first delivery channel 30 away from the first port 12 has a liquid inlet 31. The second delivery channel 40 is connected to the second port 13. The liquid flows along the first delivery channel 30 and the liquid inlet 31 into the guide channel 23 in the impeller 20, and enters the receiving cavity 11 through the outlet 25 of the guide channel 23, and then flows from the receiving cavity 11 to the second delivery channel 40, where the second delivery channel 40 discharges the fluid.

[0049] like Figure 3 As shown, further, along the direction of the rotation axis P7, the distance between the geometric center of the inlet 31 and the geometric center of the first port 12 is f1, where 0.5mm ≤ f1 ≤ 1mm. f1 can be set to one of 0.5mm, 0.6mm, 0.7mm, 0.8mm, 0.9mm, or 1mm. This setting ensures that after the fluid enters from the inlet 31, it can flow smoothly and directionally to the first port 12 along the channel, working in conjunction with the inner ring of the first annular cover plate 211 and the arc-shaped segment 221 of the blade 22 to further enhance the stability of the flow field at the inlet 24 and reduce eddy current and impact losses. This setting takes into account both machining accuracy and assembly feasibility, meeting the tolerance range of precision machining for fluid pumps used in household appliances, and ensuring the sealing of the connection between the first delivery channel 30 and the first port 12 to prevent fluid leakage (especially on the low-pressure suction side, where leakage can easily lead to insufficient suction), thus adapting to the needs of household appliance circulation systems such as water heaters and central air conditioning.

[0050] Furthermore, the first conveying channel 30 is at least partially spaced from the plane containing the first port 12. Along the axial direction of the rotation axis P7, the plane containing the inlet 31 is perpendicular to the rotation axis P7. The first conveying channel 30 extends at least partially away from the rotation axis P7 and has a predetermined gap with the plane containing the inlet 31. The maximum value of the predetermined gap is f2, where 4mm ≤ f2 ≤ 5.5mm. f2 can be set to one of 4mm, 4.2mm, 4.4mm, 4.6mm, 4.8mm, 5mm, 5.2mm, 5.4mm, or 5.5mm. The maximum distance between the plane containing the side of the first conveying channel 30 away from the inlet 31 and the plane containing the inlet 31 is f3, where 24mm ≤ f3 ≤ 26mm. f3 can be set to one of 24mm, 24.5mm, 25mm, 25.5mm, or 26mm. The geometric center of the second port 13 is located in the plane where the inlet 31 is located, and along the direction of the rotation axis P7. The distance between the geometric center of the second port 13 and the geometric center of the accommodating cavity 11 is f4, where 10mm≤f4≤11mm. By changing the parameters of the fluid pump, the flow attitude of the fluid is adjusted. Combined with three-dimensional simulation, noise can be further reduced from the source.

[0051] like Figure 10 As shown, the pump casing 10 further includes a tongue 50, which has opposing starting and ending ends. The ending end is connected to the inner wall surface of the accommodating cavity 11. Along the direction opposite to the rotation axis P7, the distance between the outer edge of the impeller 20 and the inner wall surface of the accommodating cavity 11 is w, and along the direction from the starting end to the ending end of the tongue 50 (e.g., ...). Figure 10 The direction indicated by the middle arrow M (counterclockwise in this embodiment) gradually increases. The tongue 50 divides the pump casing 10 into a suction zone near the beginning of the tongue 50 and a discharge zone near the end of the tongue 50. The gradual increase in w reduces leakage of high-pressure liquid from the discharge zone to the suction zone through the gap, allows the pressure difference between the suction and discharge zones to be released smoothly along the direction of the beginning and end of the tongue 50, prevents fluid from impacting the cavity wall or generating eddy currents after being thrown out of the impeller 20, reduces noise generation and backflow loss at the source, and also helps to improve volumetric efficiency.

[0052] The tongue 50 has a placement angle β, where 35°≤β≤40°. β can be set to one of 35°, 36°, 37°, 38°, 39°, or 40°. The tongue 50 effectively prevents high-pressure liquid from flowing back from the discharge zone to the suction zone. If β < 35°, the starting end of the tongue 50 will be excessively biased towards the rotation direction of the impeller 20, causing the suction zone to be squeezed and narrowed, increasing the inlet resistance, and making it easier for high-pressure liquid to leak back into the suction zone through the gap, resulting in backflow loss. If β > 40°, the angle between the starting end of the tongue 50 and the rotation direction of the impeller 20 is too large, and the liquid is prone to generating eddies. These eddies will impact the impeller 20 in the opposite direction, not only increasing hydraulic losses but also disrupting the pressure difference balance between the suction and discharge zones, indirectly exacerbating the risk of backflow. When 35°≤β≤40°, it ensures that the suction zone has a sufficient flow cross-section while reducing backflow loss and noise generation.

[0053] Specifically, an eight-section design method was adopted, and the range of the tongue placement angle was determined based on the specific rotational speed. Then, through multiple design simulation iterations, the simulation results are as follows: Figure 9 All turbulent kinetic energy values ​​are less than 2, confirming that the tongue placement angle is 35°≤β≤40°.

[0054] Starting from the eighth section, sections are arranged at 45° intervals, namely the seventh, sixth, fifth, fourth, third, second, and first sections. Each section is a rectangular spiral chamber with chamfered edges, and the cross-sectional area increases progressively from the first to the eighth section. (See also...) Figure 11 The length E1 of the first cross-section is 13mm-13.5mm, the width T1 is 1.5mm-2mm, and the area S1 is 18mm². 2 -21mm². See also Figure 12The length E2 of the second cross-section is 13mm-14.5mm, the width T2 is 3mm-3.5mm, and the area S2 is 35mm². 2 -43mm 2 See also Figure 13 The length E3 of the third section is 13mm-14.5mm, the width T3 is 4.5mm-5.2mm, and the area S3 is 55mm². 2 -70mm 2 See also Figure 14 The length E4 of the fourth section is 13mm-14.5mm, the width T4 is 5.5mm-6.5mm, and the area S4 is 75mm². 2 -82mm 2 See also Figure 15 The length E5 of the fifth section is 13.5mm-14.5mm, the width T5 is 7mm-8mm, and the area S5 is 95mm². 2 -102mm 2 See also Figure 16 The length E6 of the sixth section is 13.5mm-14.5mm, the width T6 is 8mm-9mm, and the area S6 is 105mm². 2 -118mm 2 See also Figure 17 The length E7 of the seventh section is 13.5mm-14.5mm, the width T7 is 9.5mm-10mm, and the area S7 is 125mm². 2 -135mm 2 See also Figure 18 The length E8 of the eighth section is 13.5mm-14.5mm, the width T8 is 11.5mm-12.5mm, and the area S8 is 145mm². 2 -155mm 2 .

[0055] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0056] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this application.

[0057] The above are merely preferred embodiments of this application and are not intended to limit this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A fluid pump, characterized in that, include: A pump housing, wherein the pump housing is provided with a receiving cavity, a first port and a second port, both the first port and the second port being connected to the receiving cavity; An impeller includes a connecting component and multiple blades. The connecting component is rotatably disposed within the receiving cavity. The multiple blades are radially connected to the connecting component around its rotation axis, and a flow channel is formed between adjacent blades. The flow channel has an inlet located near the rotation axis and an outlet located away from the rotation axis. The inlet communicates with a first port, and the outlet communicates with a second port through the receiving cavity. The blade includes at least one arcuate segment and a straight segment along a direction opposite to the axis of rotation, with the straight segment located at the tail of the blade.

2. The fluid pump according to claim 1, characterized in that, Along the direction opposite to the axis of rotation, the arc length of the arc segment is L1, and the length of the straight segment is L2, wherein L1 and L2 satisfy the relationship: 1 / 6 ≤ L2 / (L1+L2) ≤ 1 / 4; and / or, Along a direction opposite to the axis of rotation, the width of the blade gradually decreases; and / or, The straight section extends to the outer edge of the connecting member in a direction opposite to the axis of rotation.

3. The fluid pump according to claim 1, characterized in that, A straight line perpendicular to the axis of rotation and passing through the end of the arc segment near the axis of rotation is a first straight line, and a straight line perpendicular to the axis of rotation and passing through the end of the straight segment away from the axis of rotation is a second straight line. The angle formed by the intersection of the first straight line and the second straight line is α, and α satisfies the relationship: 90°≤a≤120°.

4. The fluid pump according to claim 1, characterized in that, The connecting component includes a first circle, and the ends of each arc segment near the axis of rotation are all on the outer edge contour of the first circle. The tangent of the blade through the end of the arc segment near the axis of rotation is a third straight line, and the tangent of the first circle through the end of the arc segment near the axis of rotation is a fourth straight line. The angle formed by the intersection of the third straight line and the fourth straight line is b1, where b1 satisfies the relationship: 20°≤b1≤35°; and / or, The connecting component includes a second circle, and the ends of each straight segment away from the axis of rotation are all on the outer edge contour of the second circle. The tangent of the blade through the end of the straight segment away from the axis of rotation is a fifth straight line, and the tangent of the second circle through the end of the straight segment away from the axis of rotation is a sixth straight line. The angle formed by the intersection of the fifth straight line and the sixth straight line is b2, and b2 satisfies the relationship: 35°≤b2≤50°.

5. The fluid pump according to claim 1, characterized in that, Along the direction of the rotation axis, the connecting component includes a first annular cover plate and a second annular cover plate spaced apart. The axis of the first annular cover plate, the axis of the second annular cover plate, and the rotation axis coincide. The blade is connected between the first annular cover plate and the second annular cover plate. The inner ring wall of the first annular cover plate forms a first channel. The inlet of the guide channel is connected to the first port through the first channel.

6. The fluid pump according to claim 5, characterized in that, The outer diameters of both the first and second annular cover plates are d1, where 68mm ≤ d1 ≤ 74mm; and / or, The side of the first annular cover plate closest to the second annular cover plate is designated as the first side, and the side of the second annular cover plate closest to the first annular cover plate is designated as the second side. At least a portion of the outer ring of the first side closest to the first annular cover plate and at least a portion of the outer ring of the second side closest to the second annular cover plate are parallel to each other and perpendicular to the axis of rotation, respectively; and / or, The diameter of the inner ring of the first annular cover plate is d2, 20mm≤d2≤24mm; and / or, The side of the second annular cover plate closest to the first annular cover plate is the second side, and at least a portion of the inner ring of the second side near the second annular cover plate forms an annular planar region, which is perpendicular to the axis of rotation. And / or, Along the axial direction of the rotation axis, the minimum distance between the outer edges of the first annular cover and the second annular cover is c1, where 2mm ≤ c1 ≤ 3mm; and / or, The maximum width of the blade is c2, where 9mm ≤ c2 ≤ 10mm; and / or, The end of the arc-shaped segment near the axis of rotation extends to the inner ring wall of the first annular cover plate.

7. The fluid pump according to claim 6, characterized in that, Along the radial direction of the annular plane region, the distance from the outer ring to the inner ring of the annular plane region is c3, and c3 satisfies the relationship: 8.2mm < c3 < 8.4mm.

8. The fluid pump according to any one of claims 1 to 7, characterized in that, Also includes: A first conveying channel is connected to the first port, and the end of the first conveying channel away from the first port has a liquid inlet. The second conveying channel is connected to the second port.

9. The fluid pump according to claim 8, characterized in that, Along the direction of the rotation axis, the distance between the geometric center of the inlet and the geometric center of the first port is f1, 0.5mm ≤ f1 ≤ 1mm; and / or, The first conveying channel is at least partially spaced from the plane containing the first port along the axial direction of the rotation axis. The plane containing the liquid inlet is perpendicular to the rotation axis. The first conveying channel extends at least partially away from the rotation axis and has a predetermined gap with the plane containing the liquid inlet. The maximum value of the predetermined gap is f2, where 4mm ≤ f2 ≤ 5.5mm; and / or, The maximum distance between the plane on the side of the first conveying channel away from the liquid inlet and the plane on which the liquid inlet is located is f3, where 24mm≤f3≤26mm.

10. The fluid pump according to claim 8, characterized in that, The geometric center of the second port is located in the plane where the liquid inlet is located, and along the direction of the rotation axis. The distance between the geometric center of the second port and the geometric center of the accommodating cavity is f4, where 10mm≤f4≤11mm.

11. The fluid pump according to any one of claims 1 to 7, characterized in that, The pump casing includes a tongue with opposite starting and ending ends. The ending end is connected to the inner wall of the accommodating cavity. Along the direction opposite to the rotation axis, the distance between the outer edge of the impeller and the inner wall of the accommodating cavity is w, and w gradually increases along the direction from the starting end to the ending end of the tongue.

12. The fluid pump according to claim 11, characterized in that, The tongue has a tongue placement angle β, 35°≤β≤40°.

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