A guide vane, centrifugal impeller, drainage pump and overhead machine

Abstract

The application provides a guide vane, a centrifugal impeller, a drainage pump and a canopy machine, and relates to the technical field of the canopy machine, which solves the technical problem that the lift and flow of the drainage pump under the canopy machine are limited by height. The centrifugal impeller comprises a guide vane, one side of the guide vane is outwardly convex to form an arc-shaped pressure surface, and the other side is inwardly concave to form an arc-shaped suction surface; the convex direction of the arc-shaped pressure surface is the same as the rotation direction of the centrifugal impeller, so as to form a backward arc-shaped guide vane; the drainage pump comprises a volute, the volute has a water inlet and a water outlet, and the centrifugal impeller is installed in the volute; the throat of the volute is a circular arc gradually expanding type. The application adopts the arc-shaped backward guide vane, the rounded corner design of the edges of the top and bottom of the blade, and the circular arc type volute, so that the flow process is stable, turbulence is not easy to be generated, the liquid flow speed is stable, the operation efficiency and the lift of the water pump are greatly improved, and noise is not easy to be generated.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of patio machine, in particular to a guide vane, centrifugal impeller, drainage pump and patio machine. BACKGROUND

[0002] When the patio machine is running in the refrigeration mode, a large amount of condensate water is formed on the surface of the condenser due to the water vapor in the air meeting the cold, and finally flows into the special water collecting container below the condenser. In order to discharge the condensate water in the water collecting container to the predetermined position, a drainage pump is installed beside the water collecting container of the patio machine. Due to the special installation position and structural design of the patio machine, such drainage pump not only requires a higher head, but also has certain limitations on the operating noise of the whole machine pump. SUMMARY

[0003] The purpose of the present application is to provide a guide vane, centrifugal impeller, drainage pump and patio machine to solve the technical problem that the head and flow of the drainage pump below the patio machine are limited by height in the prior art.

[0004] To achieve the above-mentioned purpose, the present application provides the following technical solutions:

[0005] In a first aspect, the present application provides a guide vane, one side of which protrudes outward to form an arc-shaped pressure surface, and the other side is recessed inward to form an arc-shaped suction surface; the protruding direction of the arc-shaped pressure surface is the same as the rotation direction of the guide vane to form a backward arc-shaped guide vane; the arc-shaped pressure surface and the arc-shaped suction surface are composed of two segments of different arc lengths arranged eccentrically through the center; wherein the center of the arc-shaped pressure surface is Q1, and the center of the arc-shaped suction surface is Q2.

[0006] The guide vane provided by the present application is a high-lift and high-flow pump vane, which can solve the problem that the head and flow of the drainage pump are limited by height by using an arc-shaped backward guide vane, and greatly improves the head and flow of the drainage pump.

[0007] Further, the center Q1 of the arc-shaped pressure surface has coordinates D1 and H1, and the center Q2 of the arc-shaped suction surface has coordinates D2 and H2; wherein: D1 [23mm, 24mm], H1 [6mm, 7.5mm], D2 [22.5mm, 24mm], H2 [8.5mm, 10mm].

[0008] Further, the initial angle of the arc line of the arc-shaped pressure surface is θ, and the initial angle of the arc line of the arc-shaped suction surface is γ, wherein: 0 [29°, 31°], γ [26°, 28°].

[0009] Further, the trajectory arc length L1 of the arc-shaped pressure surface and the trajectory arc length L2 of the arc-shaped suction surface are obtained by the following formula:

[0010] L1 = πR1α / 180;

[0011] L2 = πR2β / 180;

[0012] Wherein: α is the included angle corresponding to the trajectory arc length L1 of the arc-shaped pressure surface, α ∈ [28°, 32°]; β is the included angle corresponding to the trajectory arc length L2 of the arc-shaped suction surface, β ∈ [30°, 33°], R1 is the radius of the arc-shaped pressure surface, R1 ∈ [26.5mm, 28mm]; R2 is the radius of the arc-shaped suction surface, R2 ∈ [23.5mm, 25mm].

[0013] Further, the guide vane of the pump further comprises a vane top, a vane bottom, a leading edge and a trailing edge respectively located at the top, the bottom, the front side and the rear side of the arc-shaped pressure surface and the arc-shaped suction surface.

[0014] The height of the leading edge is H3, and the height of the trailing edge is H4, H4 ∈ [45% H3, 55% H3];

[0015] The vane top is a curved surface structure, and the height of each part of the curved surface of the vane top is obtained by the following formula:

[0016] h(x) = -(p1x 3 +p2x 2 +p3x+p4), wherein: P1, P2, P3, P4 are constants, p1 ∈ (0.0009553, 0.0009707), p2 ∈ (-0.04976, -0.04875), p3 ∈ (0.8289, 0.8504), p4 ∈ (-3.808, -3.659); x is the horizontal distance between the vane top and the leading edge.

[0017] Further, the edges of the vane top and / or the vane bottom are circular arc chamfer structures.

[0018] The guide vane of the pump provided by the application is the guide vane of the drainage pump, the edges of the vane top and the vane bottom are designed with chamfering, the flow process is stable and turbulence is not easy to occur under the condition that the flow of the impeller is difficult to be disturbed during operation, the liquid flow speed is stable, the operating efficiency and lift of the water pump are greatly improved, and noise is not easy to occur.

[0019] In a second aspect, the present application provides a centrifugal impeller, comprising an inner flow guide wall and a plurality of backward multi-wing profile flow guide pump blades formed on the inner flow guide wall, wherein the flow guide pump blades are as described above, and the flow guide pump blades are uniformly distributed around the shaft center of the centrifugal impeller.

[0020] The centrifugal impeller provided by the present application has smooth liquid flow process, is not prone to flow separation, improves the operation efficiency of the water pump, increases the centrifugal force of the pump blade operation, and thus effectively improves the water pump head and flow effect.

[0021] Further, the centrifugal impeller further comprises a water pressure ring formed on the outer edge of the inner flow guide wall, the connecting line of the trailing edges of all the flow guide pump blades forms a water discharge ring, and the water discharge ring and the inner wall of the water pressure ring have a spacing to form a water discharge ring arc length spacing.

[0022] Further, the trajectory arc length L3 of the water discharge ring arc length spacing is obtained by the following formula:

[0023] L3=πR5μ / 180;wherein:

[0024] The center of the trajectory arc length L3 coincides with the center of the blade middle arc of the flow guide pump blade;

[0025] R5 is the arc length radius of the arc length L3, and R5∈[12mm, 13mm];

[0026] μ is the arc length central angle of the arc length L3, and μ∈[8°, 12°].

[0027] In a third aspect, the present application provides a drainage pump, comprising a volute, the volute having a water inlet and a water outlet, and the centrifugal impeller being installed in the volute.

[0028] The drainage pump provided by the present application adopts a multi-wing backward arc line type flow guide design, which greatly improves the head and flow of the drainage pump while ensuring that the noise value of the drainage pump is small and the blade working area is large.

[0029] Further, the volute has a volute throat at the inside of the water outlet, and the volute throat is a circular arc gradually expanding type.

[0030] The drainage pump provided by the present application can improve the vortex of the volute water outlet caused by liquid counter pressure by adopting a circular arc type necked volute, reduce the counter pressure resistance of the volute, and achieve the effect of increasing the head and flow.

[0031] Further, the water inlet height of the volute throat is H x ∈[5.5mm, 7mm], and the optimal execution height H x= 6.1mm; the outlet height of the volute throat is H d ∈[7mm, 9mm], the optimal execution height H d = 8mm; the distance between the inlet and outlet of the volute throat is D w ∈[7mm, 9mm], the optimal execution distance D w = 6.7mm; the circular arc gradually expanding arc length L of the volute throat w central angle ∈[16°, 18°], the optimal execution angle ∈=17°, wherein the circular arc gradually expanding arc length L of the volute throat w satisfies the following formula:

[0032] L w = πR w / 180, wherein R W is the circular arc gradually expanding arc length of the volute throat.

[0033] In a fourth aspect, the application provides a patio machine, comprising a condenser, a water collecting container and a drainage pump.

[0034] Further, the water collecting container is arranged below the condenser, and the drainage pump is installed beside the water collecting container. BRIEF DESCRIPTION OF DRAWINGS

[0035] In order to more clearly illustrate the technical solutions in the embodiments of the application or the prior art, the following will briefly introduce the drawings needed to be used in the embodiments or prior art description. Obviously, the drawings in the following description only constitute some embodiments of the application, and for those skilled in the art, other drawings can also be obtained without creative labor based on these drawings.

[0036] Figure 1 is a schematic view of the cross-sectional structure of the drainage pump of the application;

[0037] Figure 2 is a schematic view of the three-dimensional structure of the centrifugal impeller in the drainage pump of the application;

[0038] Figure 3 is a schematic view of the cross-sectional structure of the centrifugal impeller in the drainage pump of the application;

[0039] Figure 4 is an enlarged view of the local structure of the centrifugal impeller in the drainage pump of the application;

[0040] Figure 5 is a sketch of the blade profile section of the centrifugal impeller of the application;

[0041] Figure 6 is an enlarged view of the local structure of the blade of the centrifugal impeller of the application;

[0042] Figure 7 is a schematic view of the blade structure of the centrifugal impeller in the drainage pump of the present application;

[0043] Figure 8 is a schematic view of the three-dimensional structure of the volute in the drainage pump of the present application;

[0044] Figure 9 is a schematic view of the cross-sectional structure of the volute in the drainage pump of the present application;

[0045] Figure 10 is a comparison curve of the head and flow rate of the new and original drainage pumps;

[0046] Figure 11 is a schematic view of the end surface structure of the centrifugal impeller from one end.

[0047] Figure 12 is a schematic view of the structure of the volute throat in the drainage pump of the present application.

[0048] In the figure, 1 is the pump body base; 2 is the driving direct current motor; 3 is the motor heat dissipation support; 4 is the volute; 5 is the centrifugal impeller; 6 is the rotating shaft; 7 is the spline; 8 is the flow guide pump blade; 9 is the water pressure ring; 11 is the arc line type pressure surface; 12 is the arc line type suction surface; 13 is the blade top; 15 is the blade bottom; 16 is the leading edge; 17 is the trailing edge; 18 is the circular arc chamfer; 19 is the volute throat; 20 is the water inlet; 21 is the water outlet; 22 is the blade middle arc line; 23 is the arc length interval of the water discharge ring; 24 is the water discharge ring. DETAILED DESCRIPTION

[0049] In order to make the purpose, technical scheme and advantages of the present application more clear, the technical scheme of the present application will be described in detail below. Obviously, the described embodiments are only some of the embodiments of the present application, but not all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of the present application.

[0050] Embodiment 1:

[0051] The flow guide pump blade in the centrifugal impeller of the drainage pump in the prior art is a straight line type blade, and since the drainage pump is installed near the patio machine located on the top of the house, there is a certain installation height, which causes the drainage pump of the patio machine to have low head and flow rate, and cannot meet the drainage problem of the drainage pump of some users in special installation environment. In order to solve this problem, the flow guide pump blade in the centrifugal impeller of the drainage pump of the present application is designed as an arc line type blade. Figures 2-6As shown, this invention provides a novel guide pump blade for a centrifugal impeller. Specifically, one sidewall of the guide pump blade protrudes outward in an arc shape to form an arc-shaped pressure surface 11, while the opposite sidewall on the other side is concave in an arc shape to form an arc-shaped suction surface 12. By adopting this novel arc-shaped guide pump blade, the head and flow rate of the drainage pump are significantly improved. Furthermore, the protrusion direction of the arc-shaped pressure surface 11 is the same as the rotation direction of the guide pump blade. Since this guide pump blade is a guide pump blade on a centrifugal impeller 5, the protrusion direction of its arc-shaped pressure surface 11 is the same as the rotation direction of the centrifugal impeller 5, forming a backward arc-shaped guide pump blade. This blade design facilitates liquid flow, reduces vortex formation, increases the working area, and thus improves the head and flow rate.

[0052] Furthermore, in this embodiment, the curvature of the arc-shaped pressure surface 11 (i.e., the convex surface) and the curvature of the arc-shaped suction surface 12 (i.e., the concave surface) can be the same or different. They can be formed by two arcs with different radii located at the same center, so that the overall width of the guide pump blade is equal. They can also be formed by using arcs with different curvatures at the beginning, middle and end sections to form the entire arc-shaped pressure surface 11 or arc-shaped suction surface 12.

[0053] Of course, the arc shape of the arc-shaped pressure surface 11 and the arc-shaped suction surface 12 is not limited to the above-mentioned types. As long as they are arc-shaped pressure surfaces and suction surfaces, they are acceptable. In this embodiment, no specific limitation is made.

[0054] The guide pump impeller provided by this invention is a high-head, high-flow pump impeller. By adopting an arc-shaped rearward guide pump impeller, the problem of the head and flow rate of the drainage pump being limited by height can be solved, and the head and flow rate of the drainage pump can be greatly improved.

[0055] Example 2:

[0056] The difference between this embodiment 2 and embodiment 1 is that, in this embodiment, the arc structure forming the arc-shaped pressure surface 11 and the arc-shaped suction surface 12 is specifically defined.

[0057] like Figure 3 As shown, specifically, the arc-shaped pressure surface 11 and the arc-shaped suction surface 12 are composed of two segments of different arc lengths arranged eccentrically around the center. That is to say, the arc lengths of the arc-shaped pressure surface 11 and the arc-shaped suction surface 12 are not the same, one is longer and the other is shorter, and the centers of the arcs corresponding to the arc-shaped pressure surface 11 and the arc-shaped suction surface 12 are not the same. The two centers are offset, and the centers do not pass through the central axis of the centrifugal impeller 5, but are eccentrically set; among them, the center of the arc-shaped pressure surface 11 is Q1, and the center of the arc-shaped suction surface 12 is Q2.

[0058] In the present application, the center Q1 of the arc pressure surface 11 has coordinates (D1, H1), and the center Q2 of the arc suction surface 12 has coordinates (D2, H2); that is, the center coordinates Q1 and Q2 are determined by D1, H1, D2, and H2. It should be noted that D1 and D2 are the coordinates corresponding to the X axis, and H1 and H2 are the coordinates corresponding to the Y axis, and the origin of the XY axis coordinates is located at the center axis of the centrifugal impeller 5.

[0059] Through a large number of experimental tests, the data range of D1, H1, D2, and H2 is obtained as follows: D1 ∈ [23 mm, 24 mm], the optimal execution distance D1 = 23.51 mm; H1 ∈ [6 mm, 7.5 mm], the optimal execution distance H1 = 6.96 mm; D2 ∈ [22.5 mm, 24 mm], the optimal execution distance D2 = 23.23 mm; H2 ∈ [8.5 mm, 10 mm], the optimal execution distance H2 = 9.41 mm.

[0060] As shown in Figure 5 Further, the initial angle of the arc of the arc pressure surface 11 is θ, and specifically, θ is the angle between the starting point position of the arc pressure surface 11 and the horizontal plane. The initial angle of the arc of the arc suction surface 12 is γ, and specifically, γ is the angle between the starting point position of the arc suction surface 12 and the horizontal plane. That is, the initial positions of the trajectory arc lengths L1 and L2 of the guide pump blade are determined by θ and γ, respectively.

[0061] Through a large number of experimental tests, the angle range of θ and γ is obtained as follows: θ ∈ [29°, 31°], the optimal execution angle θ = 30.3°; γ ∈ [26°, 28°], the optimal execution angle γ = 27.1°.

[0062] Further, the trajectory arc length L1 of the arc pressure surface 11 and the trajectory arc length L2 of the arc suction surface 12 are calculated by the following formulas:

[0063] L1 = πR1α / 180; (1)

[0064] L2 = πR2β / 180; (2)

[0065] As shown in Figure 3 and Figure 4 α is the angle corresponding to the trajectory arc length L1 of the arc pressure surface 11, α ∈ [28°, 32°]; β is the angle corresponding to the trajectory arc length L2 of the arc suction surface 12, β ∈ [30°, 33°]; R1 is the radius of the arc pressure surface 11, R1 ∈ [26.5 mm, 28 mm]; and R2 is the radius of the arc suction surface 12, R2 ∈ [23.5 mm, 25 mm].

[0066] In summary, the profile of the guide pump impeller of the present invention, i.e., the rearward guide pump impeller, is determined by the arc-shaped pressure surface 11 and the arc-shaped suction surface 12. The blade thickness and trajectory are determined by different centers Q1 and Q2 and different radii R1 and R2 eccentricities. Furthermore, as... Figure 3 As shown, the arc lengths L1 and L2 of the guide pump blade trajectory are determined by α and β, and the arc lengths L1 and L2 satisfy the above relationships (1) and (2).

[0067] After calculation, the trajectory arc length L1 of the arc-shaped pressure surface 11 is within the following range: L1∈[13mm, 14mm], with an optimal execution distance L1=14.15mm; the trajectory arc length L2∈[13mm, 14mm] of the arc-shaped suction surface 12 is an optimal execution distance L2=13.42mm; R1∈[26.5mm, 28mm], with an optimal execution distance R1=27.1mm; R2∈[23.5mm, 25mm], with an optimal execution distance R2=24.27mm; α∈[28°, 32°], with an optimal execution angle α=29.1°; β∈[30°, 33°], with an optimal execution angle β=31.7°.

[0068] like Figure 6 As shown, the guide pump blade of the present invention also includes a blade top 13, a blade bottom 16, a leading edge 16, and a trailing edge 17 located at the top, bottom, front side, and rear side of the arc-shaped pressure surface 11 and the arc-shaped suction surface 12, respectively.

[0069] The blade tip 13, blade bottom 16, leading edge 16, trailing edge 17, arc-shaped pressure surface 11, and arc-shaped suction surface 12 together form a complete guide pump blade;

[0070] In this embodiment, as Figure 7 As shown, the height of the leading edge 16 is H3, and the height of the trailing edge is H4, where: H4∈[45%H3, 55%H3];

[0071] like Figure 7 As shown, the top 13 of the blade has a curved surface structure. That is to say, the outer contour geometry of the guide pump blade is composed of curves, H3 and H4 and the bottom. The height of the guide pump blade is determined by the leading edge 16 and the trailing edge 17. H3 determines the height of the leading edge 16 and H4 determines the height of the trailing edge 17. H3 = h, H4 ∈ [45% H3, 55% H3]. The head has a greater impact. The head increases with the increase of h. The optimal operating height h = 6.81 mm.

[0072] Furthermore, the height of each part of the blade tip surface, i.e., the curve, is determined by the function curve and the height of the leading edge 16. The function curve satisfies the following formula, which means that the height of each part of the blade tip surface is calculated using the following formula:

[0073] h(x) = -(p1x)3 +p2x 2 +p3x+p4), (3)

[0074] Where: P1, P2, P3, and P4 are all constants, p1∈(0.0009553, 0.0009707), p2∈(-0.04976, -0.04875), p3∈(0.8289, 0.8504), and p4∈(-3.808, -3.659); x is the horizontal distance between the tip and the leading edge of the blade.

[0075] After extensive testing and analysis, the optimal function input is:

[0076] h(x)=-(0.000963x 3 -0.04926x 2 +0.8397x-3.733); (4)

[0077] Furthermore, the edges of the blade tip and / or blade base are rounded and chamfered.

[0078] Specifically, such as Figure 4 As shown, all edge junctions on the starting side of the blade tip 13 and blade bottom 15 are R3 rounded chamfered structures, and all edge junctions on the ending side of the blade tip 13 and blade bottom 15 are R4 rounded chamfered structures.

[0079] The edges of the top 13 and bottom 15 of the arc-shaped rearward guide pump impeller of the present invention are chamfered with R3 and R4, respectively. Compared with the case where the edges are not chamfered, the flow is less likely to be turbulent when the impeller is working, thus making the flow process smooth and less likely to cause flow separation. This makes the liquid flow speed stable, which is beneficial to improving the operating efficiency of the water pump and is less likely to generate operating noise.

[0080] The guide pump impeller provided by this invention is a guide pump impeller for a drainage pump. The top and bottom edges of the impeller are rounded, which ensures that the flow is not disturbed during impeller operation, making the flow process smooth and less prone to turbulence. This results in a stable liquid flow speed, significantly improving the pump's operating efficiency and head, and reducing noise generation.

[0081] Example 3:

[0082] In this embodiment, as Figure 2 As shown, the present invention provides a centrifugal impeller 5, including an inner guide wall and a plurality of backward multi-blade guide pump blades 8 formed on the inner guide wall, the structure of the guide pump blades 8 being as described in Embodiments 1 and 2.

[0083] In the embodiment, the plurality of guide vanes 8 are evenly distributed around the shaft of the centrifugal impeller 5, and the leading edges of the guide vanes 8 are close to the shaft, and the trailing edges are close to the outer edge of the inner guide wall.

[0084] The centrifugal impeller provided by the application has the advantages that the guide vanes are designed in the backward multi-wing arc line type, the liquid flow is smooth, flow separation is not easy to occur, the operation efficiency of the water pump is improved, the centrifugal force of the pump blade during operation is increased, and the water pump lift and flow are effectively improved.

[0085] Further, as shown in Figure 2 and Figure 11 , the centrifugal impeller 5 further comprises a water pressure ring 9 formed at the outer edge of the inner guide wall, the trailing edges 17 of all the guide vanes 8 are connected to form a water discharge ring 24, the water discharge ring 24 is not a solid structure, but a circular ring structure formed by connecting all the trailing edges 17, and the water discharge ring 24 has a spacing between the inner wall of the water pressure ring 9 to form a water discharge ring arc length spacing 23.

[0086] The trajectory arc length L3 of the water discharge ring arc length spacing 23 is obtained by the following formula:

[0087] L3 = πR5μ / 180; wherein:

[0088] The center of the trajectory arc length L3 is coincident with the center of the blade middle arc line 22 of the guide vane;

[0089] R5 is the arc length radius of the trajectory arc length L3, R5 ∈ [12mm, 13mm]; the optimal execution arc length radius R5 = 12.97mm;

[0090] μ is the arc length central angle of the trajectory arc length L3, μ ∈ [8°, 12°], and the optimal execution arc length central angle μ = 9.57°.

[0091] The trailing edges of the guide vanes are all located on the water discharge ring, and the water discharge ring has a spacing with the inner wall of the water pressure ring, so that the turbulence vortex generated by the work of the blade during operation is released through the water discharge ring, the contact friction between the turbulence vortex and the trailing edge of the blade during operation is effectively reduced, the impact of the turbulence pressure on the trailing edge of the blade is weakened, the working noise of the impeller during operation is reduced, and the stability of the water pump performance is improved.

[0092] As shown in Figure 1 , the shaft 6 is arranged at the shaft center of the inner guide wall, the shaft 6 is hollow inside, the spline 7 is arranged in the top inner cavity of the shaft 6, and the spline 7 connects the shaft 6 with the motor shaft of the driving direct-current motor 2.

[0093] Embodiment 4:

[0094] As shown in Figure 1 , Figure 8 ,Figure 9 As shown in the drawings, in this embodiment, the application provides a drainage pump, which comprises a pump body base 1, a driving direct current motor 2, a motor heat dissipation support 3, and a volute 4; the driving direct current motor 2 is installed in the pump body base 1; the motor heat dissipation support 3 is installed between the volute 4 and the driving direct current motor 2, and is used for heat dissipation of the driving direct current motor 2; the volute 4 has a medium flow channel inside, for medium flow; the volute 4 has a water inlet 20 at the bottom and a water outlet 21 at the side; a centrifugal impeller 5 is installed in the medium flow channel in the volute 4, and is used for pumping the medium into the water inlet 20 and then pumping the medium out of the water outlet 21. It should be noted that the centrifugal impeller 5 in this embodiment is the centrifugal impeller in Embodiment 3.

[0095] The drainage pump provided by the application adopts a multi-wing backward arc line type flow guide design, which greatly improves the lift and flow of the drainage pump while ensuring that the noise value of the drainage pump is small and the blade working area is large.

[0096] Further, as shown in Figure 1 and Figure 9 , the volute 4 has a volute throat 19 at the position on the inner side of the water outlet 21; in order to reduce the vortex caused by the reverse pressure of the liquid at the water outlet of the volute and reduce the reverse pressure resistance of the volute, the volute throat 19 is provided with a circular arc chamfer 18, thereby forming a circular arc gradually expanding type neck-in structure.

[0097] It should be noted that, as shown in Figure 9 , the circular arc gradually expanding type neck-in is a circular arc curved surface in the circumferential direction at the outlet position of the volute throat; the axial chord line of the outlet position cross section is a circular arc curve.

[0098] As shown in Figure 12 , further, the water inlet height of the volute throat is H T ∈[5.5mm, 7mm], the optimal execution height H x =6.1mm; the water outlet height of the volute throat is H d ∈[7mm, 9mm], the optimal execution height H d =8mm; the distance between the water inlet and the water outlet of the volute throat is D w ∈[7mm, 9mm], the optimal execution distance D w =6.7mm; the circular arc gradually expanding arc length L w of the volute throat satisfies the following formula: w

[0099] L w =πR w ε / 180, wherein R W ​The arc length of the circular arc gradually expanding throat of the volute.

[0100] The drainage pump provided by the application can improve vortex caused by liquid reverse pressure at the water outlet of the volute, reduce reverse pressure resistance of the volute, and increase lift and flow.

[0101] Embodiment 5

[0102] The drainage pump provided by the application can improve vortex caused by liquid reverse pressure at the water outlet of the volute, reduce reverse pressure resistance of the volute, and increase lift and flow.

[0103] It should be noted that the drainage pump in the embodiment adopts the drainage pump in Embodiment 4.

[0104] The volute throat 19 of the volute 4 in the prior art is designed in a straight line gradually expanding manner, and the volute throat 19 is improved to be designed in a circular arc gradually expanding manner in the application, so that the problem that liquid pressure cannot be fully released in the straight line gradually expanding structure, liquid pressure is accumulated at the volute throat, liquid pressure at the throat is converted into reverse pressure resistance with the increase of pressure, and vortex is finally generated, and the performance of the water pump is greatly attenuated, is solved. By adopting the circular arc gradually expanding volute throat, the problem of reverse pressure vortex formed at the water outlet is improved, the resistance of the water outlet of the volute is reduced, the operation efficiency of the water pump is improved, and the performance of the water pump is optimized.

[0105] Specifically, in the embodiment, the structure of the drainage pump is as shown in Figure 1 and includes a pump body base 1, a driving direct current motor 2, a motor heat dissipation support 3, a volute 4, and a centrifugal impeller 5. The driving direct current motor 2 is located between the pump body base 1, the motor heat dissipation support 3 is assembled and connected with the volute 4 through screws, the centrifugal impeller 5 is located in the cavity of the volute 4, is connected with the driving direct current motor shaft, and rotates and operates with the driving direct current motor 2. The centrifugal impeller 5 has a great influence on the performance of the drainage pump. The structure of the centrifugal impeller 5 is as shown in Figure 2 and is composed of a rotating shaft 6, a spline 7, an arc line type backward guide pump blade 8, and a water pressure ring 9.

[0106] As shown in Figure 6 the structure of the guide pump blade 8 is composed of a blade top 13, a blade bottom 15, an arc line type pressure surface 11, an arc line type suction surface 12, a leading edge 16, and a trailing edge 17.

[0107] The structure of the volute 4 is as shown in Figure 8 and is composed of a water inlet 20, a water outlet 21, a circular arc chamfer 18, and a volute throat 19.

[0108] The drainage pump provided by the application is a drainage pump with high-lift, high-flow pump blades and a circular-arc necked volute, has stable flow and is not prone to flow separation during operation, improves the operation efficiency of the drainage pump, increases the centrifugal force of the pump blades during operation, and thus effectively improves the lift and flow of the water pump.

[0109] Comparison of new drainage pump and original drainage pump data:

[0110] The test results shown in the following table are obtained through experiments. Figure 10 As can be seen from the attached Figure 10 , the new drainage pump has higher lift at the same flow, especially at high lift, and has a significant advantage in flow compared to the original drainage pump, and the flow fluctuates less with the increase of lift, and in addition, the flow can be increased by about 32.13% at the same high lift.

[0111] Table 1 below is a performance comparison table of the new drainage pump and the original drainage pump.

[0112] Table 1: Performance comparison of new and original drainage pumps

[0113] Drain pump 1.2 m flow / mL Head / m Original drain pump 590 1.45 New drain pump 900 1.65

[0114] As can be seen from the experimental data in Table 1, the performance of the new drainage pump provided by the application is improved by 13.8% under the same test conditions. The experimental data shows that the new drainage pump of the application has a significant advantage in performance, and can effectively solve the problem of height limitation of drainage pump lift and flow, and greatly improve the operation efficiency of the drainage pump.

[0115] First of all, it should be noted that "inward" is the direction towards the center of the accommodation space, and "outward" is the direction away from the center of the accommodation space.

[0116] In the description of the application, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate the orientation or positional relationship based on the drawings, and are only used to facilitate the description of the application and simplify the description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation of the application. Figure 1

[0117] ​In addition, the terms "first", "second", or the like are used only to describe different features, and do not imply or suggest relative importance or a specific number of the features being referred to. Thus, features defined with "first", "second" can explicitly or implicitly include at least one of the features. In the description of the present application, the meaning of "a plurality of" is at least two, such as two, three, etc., unless otherwise explicitly specified and limited.

[0118] In the present application, unless otherwise explicitly specified and limited, the terms "mounting", "connecting", "connecting", "fixing" and the like should be understood broadly, for example, it can be fixed connection, or detachable connection, or integrated; it can be mechanical connection, or electrical connection; it can be directly connected, or indirectly connected through intermediate medium, it can be the internal communication of two elements or the interaction relationship of two elements, unless otherwise explicitly limited. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0119] In the present application, unless otherwise explicitly specified and limited, the first feature is "on" or "under" the second feature, which can be direct contact between the first and second features, or indirect contact between the first and second features through intermediate medium. Moreover, the first feature "above", "over" and "on" the second feature can be directly above or obliquely above the first feature, or only indicate that the horizontal height of the first feature is higher than that of the second feature. The first feature "below", "under" and "under" the second feature can be directly below or obliquely below the first feature, or only indicate that the horizontal height of the first feature is less than that of the second feature.

[0120] In the description of the present application, the description of the terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present application. In the present application, the illustrative description of the above terms is not necessarily for the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any appropriate manner in any one or more embodiments or examples. In addition, those skilled in the art can combine and combine different embodiments or features of different embodiments or examples described in the present application without contradiction.

[0121] The above is only a specific embodiment of the present application, but the protection scope of the present application is not limited thereto, any skilled in the art can easily think of changes or replacements within the technical scope disclosed by the present application, which should be covered within the protection scope of the present application. Therefore, the protection scope of the present application should be subject to the protection scope of the claims.

Claims

1. A type of guide pump impeller, characterized in that, One side of the guide pump blade protrudes outward to form an arc-shaped pressure surface, and the other side is recessed inward to form an arc-shaped suction surface; the protrusion direction of the arc-shaped pressure surface is the same as the rotation direction of the guide pump blade to form a backward arc-shaped guide pump blade. The arc-shaped pressure surface and the arc-shaped suction surface are formed by two segments of different arc lengths arranged eccentrically around a center, wherein the center of the arc-shaped pressure surface is Q1 and the center of the arc-shaped suction surface is Q2; the guide pump blade also includes blade tops, blade bottoms, leading edges, and trailing edges located at the top, bottom, front, and rear sides of the arc-shaped pressure surface and the arc-shaped suction surface, respectively; wherein: The height of the leading edge is H3, and the height of the trailing edge is H4, where H4 ∈ [45%H3, 55%H3]. The blade tip has a curved surface structure, and the height of each part of the curved surface at the blade tip is calculated using the following formula: , where: P1, P2, P3, and P4 are all constants, p1∈(0.0009553,0.0009707), p2∈(-0.04976, -0.04875), p3∈(0.8289, 0.8504), and p4∈(-3.808, -3.659); x is the horizontal distance between the tip and the leading edge of the blade.

2. The guide pump impeller according to claim 1, characterized in that, The coordinates of the center Q1 of the arc-shaped pressure surface are D1 and H1, and the coordinates of the center Q2 of the arc-shaped suction surface are D2 and H2; wherein: D1∈[23mm, 24mm], H1∈[6mm, 7.5mm], D2∈[22.5mm, 24mm], H2∈[8.5mm, 10mm].

3. The guide pump impeller according to claim 1, characterized in that, The initial angle of the arc of the arc-shaped pressure surface is θ, and the initial angle of the arc of the arc-shaped suction surface is γ, where: θ∈[29°, 31°], γ∈[26°, 28°].

4. The guide pump impeller according to claim 1, characterized in that, The arc length L1 of the arc-shaped pressure surface and the arc length L2 of the arc-shaped suction surface are calculated using the following formulas: ； ； Where: α is the included angle corresponding to the arc length L1 of the arc-shaped pressure surface, α∈[28°, 32°]; β is the included angle corresponding to the arc length L2 of the arc-shaped suction surface, β∈[30°, 33°]; R1 is the radius of the arc-shaped pressure surface, R1∈[26.5mm, 28mm]; R2 is the radius of the arc-shaped suction surface, R2∈[23.5mm, 25mm].

5. The guide pump impeller according to claim 1, characterized in that, The edges of the top and / or bottom of the blade are both rounded and chamfered.

6. A centrifugal impeller, characterized in that, It includes an inner guide wall and a plurality of backward multi-blade guide pump blades formed on the inner guide wall, the guide pump blades being as described in any one of claims 1-5.

7. The centrifugal impeller according to claim 6, characterized in that, The centrifugal impeller also includes a pressure ring formed on the outer edge of the inner guide wall, and the trailing edge of all the guide pump blades forms a drain ring. There is a gap between the drain ring and the inner wall of the pressure ring to form an arc length gap of the drain ring.

8. The centrifugal impeller according to claim 7, characterized in that, The trajectory arc length L3 of the drainage ring arc length spacing is calculated using the following formula: ;in: The center of the trajectory arc length L3 coincides with the center of the arc in the blade of the guide pump. R5 is the radius of the arc length L3 of the trajectory, R5∈[12mm, 13mm]; µ is the central angle of the arc length L3 of the trajectory, μ∈[8°, 12°].

9. A drainage pump, characterized in that, It includes a volute having an inlet and an outlet, and a centrifugal impeller as described in any one of claims 6-8 is installed inside the volute.

10. The drainage pump according to claim 9, characterized in that, The volute is located inside the outlet and has a volute throat, which is an arc-shaped, gradually expanding and constricting structure.

11. A ceiling machine, characterized in that, It includes a condenser, a water collection container, and a drain pump as described in any one of claims 9-10.

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