CN109751249B - Borderless swimming pool - Google Patents
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Abstract
The invention belongs to the field of drainage pumps, and particularly relates to a borderless swimming pool, which comprises a swimming pool body, wherein a swimming pool pump is arranged in the swimming pool body, the swimming pool pump comprises an impeller, and the impeller is an impeller with a small hub ratio. The invention has the beneficial effects that: the small hub ratio impeller has reasonable structure and excellent hydraulic performance, and compared with the traditional structure, the small hub ratio impeller reduces the hub by about 64 percent and the outer diameter of the impeller by about 13 percent under the condition that the flow and the lift meet the requirements of design working conditions, thereby obviously improving the flow capacity of the impeller.
Description
Technical Field
The invention belongs to the field of swimming pools, and particularly relates to a borderless swimming pool.
Background
Swimming is a good exercise mode, and has a very important effect on improving the cardiovascular system. The cold water stimulation can promote blood circulation through heat regulation and metabolism; in addition, the pressure and resistance of the water during swimming play a special role in the circulation of the heart and blood. Can also effectively improve the cardio-pulmonary function, enhance the endurance and improve the vital capacity.
However, the existing artificial swimming pool is generally large in volume, so that the water storage capacity is also large, and the water in the swimming pool needs to be circulated to ensure the sanitary condition and provide swimming pleasure. However, the existing swimming pool pump has large hub and impeller outer diameter, large volume and weight, poor flow capacity of the impeller and low hydraulic efficiency.
Disclosure of Invention
In order to solve the problems, the invention provides a borderless swimming pool, the outer diameters of a hub and an impeller are both smaller, the flow capacity of the impeller is better, and the hydraulic efficiency is improved.
The invention provides the following technical scheme:
a borderless swimming pool comprises a swimming pool body, wherein a swimming pool pump is arranged in the swimming pool body and comprises an impeller, and the impeller is an impeller with a small hub ratio.
Preferably, the swimming pool body is internally provided with a water inlet, a water outlet, an upper circulation flow channel, a lower circulation flow channel, a massage hole and a rectification grid, wherein the massage hole is communicated with the swimming pool pump through the upper circulation flow channel, the water outlet is communicated with the swimming pool pump through the lower circulation flow channel, and the swimming pool pump is also communicated with the water inlet.
Preferably, the swimming pool pump further comprises a driving part for driving the small hub ratio impeller to rotate, the draining pump further comprises a shell, the driving part comprises a stator assembly fixed on the shell, the driving part further comprises a rotor assembly matched with the stator assembly, the rim of the small hub ratio impeller is fixedly connected with the inner wall of the rotor assembly and rotates along with the rotor assembly, and the middle part of the small hub ratio impeller is hollow;
a water inlet and a water outlet are respectively arranged on two sides of the shell, two ends of the rotor assembly are respectively connected with the water inlet and the water outlet, the water outlet is provided with a guide vane matched with the impeller, and the water passing wall surfaces of the shell, the rotor assembly and the stator assembly are respectively provided with an anti-corrosion lining layer adopting a fluorine lining process;
the rotor assembly is located in the stator assembly through the wear-resisting ring, the upper side and the lower side of the rotor assembly are respectively provided with an outlet side sliding bearing facilitating the matching and rotation of the rotor assembly and the water outlet and an inlet side sliding bearing facilitating the matching and rotation of the rotor assembly and the water inlet, a cooling channel for cooling and lubrication is formed by enclosing the rotor assembly, the water outlet, the stator assembly and the water inlet, and an anti-corrosion lining layer adopting a fluorine lining process is arranged on the cooling channel.
Preferably, the method for designing the impeller with the small hub ratio comprises the following steps:
s1, obtaining the outer diameter D of the impeller with the small hub ratio;
s2, determining the number of blades and the blade airfoil of the impeller with the small hub ratio;
s3, obtaining the blade cascade density S at the edge of the impeller with small hub ratioyAnd blade row density s at the hubg；
S4, dividing blades of the impeller with the small hub ratio into m cylindrical sections in an equidistant mode, sequentially marking the cylindrical sections as 1-1, 2-2, … … and m-m from the hub to the edge, and respectively obtaining an airfoil arrangement angle beta of each cylindrical sectionL；
S5 for airfoil setting angle beta in S4LCorrecting the value of (A);
s6, determining the blade thickness of the impeller with the small hub ratio;
s7, modeling parameters of the impeller with the small hub ratio obtained in the S1-S6, carrying out numerical simulation on the established impeller model to obtain a simulation lift value, and if the simulation lift value is within the range of the design lift value, completing the design of the impeller with the small hub ratio;
and if the simulation lift value is out of the design lift value range, switching to S1 for recalculation until the simulation lift value is in the design lift value range.
Preferably, the specific step of S1 includes:
s11, obtaining the estimated value D of the outer diameter of the impeller with the small hub ratio by the following formulaEstimated value,
Wherein n is the motor rotation speed, pi is the circumference ratio, nsThe specific rotating speed of the rim driving pump, and H is the lift;
s12, obtaining the small hub ratio impeller hub diameter d through the following formula,
d＝Rd*Destimated value
Wherein R isdAs a hub ratio, DEstimated valueThe estimated value of the outer diameter of the small hub ratio impeller obtained in S11;
s13, obtaining the actual value D of the outer diameter of the impeller with the small hub ratio by the following formula,
wherein Q is the flow, n is the motor speed, pi is the circumferential rate, and d is the diameter of the impeller hub with the small hub ratio obtained in S12.
Preferably, the number of the blades in the S2 is 3-5, and the airfoil profile of the blade is an NACA series airfoil profile;
the actual value D of the small hub ratio impeller outer diameter obtained in S13 is checked by the following equation:
if D isCheckingWithin 0.1-0.3, is within the range of small hub ratios, if DCheckingOutside of 0.1-0.3, the outer diameter D of the impeller with a small hub ratio is retrieved through S11-S13.
Preferably, the specific step of S3 includes:
s31, obtaining the density S of the blade cascade at the wheel edge through the following formulay，
sy＝6.1751k+0.01254
Wherein,
nsthe specific speed of the rim driven pump;
s32, obtaining the blade cascade density S at the hub through the following formulag，
sg＝(1.7～2.1)sy
Preferably, the specific step of S4 includes:
s41, obtaining the inlet setting angle beta of each cylindrical section through the following formula1And outlet setting angle beta2，
Wherein, beta1' is the inlet flow angle of the liquid,
u is the peripheral speed, vmIs the flow velocity of the axial surface of the inlet of the blade,
is the coefficient of blade displacement, pi is the circumferential ratio, etavFor pump volumetric efficiency, D is the outer diameter of the impeller with small hub ratio, D is the hub diameter of the impeller with small hub ratio; delta beta1Is an entrance attack angle; beta is a2' is the outlet flow angle,
vu2being the component of the absolute velocity in the circumferential direction,
ηhthe hydraulic efficiency of the pump is shown, xi is a correction coefficient, g is the gravity acceleration, and H is the lift; delta beta2An exit attack angle;
s42, obtaining the airfoil arrangement angle beta of each cylindrical section through the following formulaL，
βL＝(β1+β2)/2
Preferably, the specific process of correcting in S5 is as follows:
respectively obtaining the inlet setting angles beta of the m cylindrical sections through the formula in S411Is selected to be closest to the rim, and the cross-sectional diameters of the three cylindrical sections closest to the rim and the corresponding inlet seating angles beta are selected1Fitting the values of (a) to obtain the following quadratic polynomial:
y1＝a1x2+b1x+c1
wherein, y1Setting an angle beta for the inlet1X is the diameter of the cross section of the cylinder, a1、b1And c1Are all constant and are all provided with the same power,
respectively substituting the section diameters of the 1 st to the mth cylindrical sections into the quadratic polynomial to obtain the corrected inlet placement angles beta of the 1 st to the mth cylindrical sections1A value of (d);
the outlet setting angles beta of the m cylindrical sections are respectively obtained by the formula in S412Is selected to be closest to the rim, the cross-sectional diameter of the three cylindrical sections closest to the rim and the corresponding outlet seating angle beta2Fitting the values of (a) to obtain the following quadratic polynomial:
y2＝a2x2+b2x+c2
wherein, y2Setting an angle beta for the outlet2X is the diameter of the cross section of the cylinder, a2、b2And c2Are all constant and are all provided with the same power,
respectively substituting the section diameters of the 1 st to the mth cylindrical sections into the quadratic polynomial to obtain the outlet setting angles beta of the 1 st to the mth cylindrical sections after being corrected2The value of (a) is,
setting the corrected inlet setting angle beta1And outlet setting angle beta2Substituting the formula in S42 to obtain the corrected airfoil setting angle beta of each cylindrical sectionLThe value of (c).
Preferably, the thickness of the blade in S6 is smaller under the condition of meeting the requirement of mechanical strength, the thickness of the blade at the wheel rim is 2 to 4 times of the thickness of the blade at the wheel hub, and the thickness of the blade at the rest part is changed in a uniform and smooth transition manner.
The invention has the beneficial effects that:
1. the swimming pool jump is embedded in the swimming pool, the water outlet is connected with the water inlet through the pipeline built in the swimming pool, the swimming pool pump is driven by the motor to work, an internal circulation can be formed in the swimming pool, the power of the motor can be changed to change the power of the pump during working, so that the flow speed of the water flow at the outlet is changed to adapt to the swimming speed of a swimmer, and the swimmer does not need to change the advancing direction frequently. And the wall of the pool is provided with massage holes, so that the water flow can impact the acupuncture points of people to achieve the massage effect.
2. The small hub ratio impeller has reasonable structure and excellent hydraulic performance, and compared with the traditional structure, the small hub ratio impeller reduces the hub by about 64 percent and the outer diameter of the impeller by about 13 percent under the condition that the flow and the lift meet the requirements of design working conditions, thereby obviously improving the flow capacity of the impeller.
Drawings
Figure 1 is a schematic view of the structure of a swimming pool;
FIG. 2 is a diagram of a massage hole water flow circulation of a swimming pool, with arrows indicating the direction of water flow;
FIG. 3 is a flow circulation diagram of a swimming pool, with arrows indicating the direction of flow;
FIG. 4 is a schematic view of a pool pump configuration;
FIG. 5 is a schematic structural view of a small hub ratio impeller blade;
FIG. 6 is a three-dimensional view of a small hub ratio impeller blade;
FIG. 7 is a flow Q-head H curve and a flow Q-efficiency eta curve of a numerical simulation of a small hub ratio impeller;
FIG. 8 is a velocity flow diagram of a numerical simulation of a low hub ratio impeller;
FIG. 9 is a total pressure profile at a mid-section of an impeller blade;
fig. 10A is a comparison of small hub ratio impeller head to model experimental head results;
FIG. 10B is a comparison of low hub ratio impeller efficiency and model experimental efficiency results;
FIG. 11 is a three-dimensional view of a small hub ratio impeller blade with the hub removed.
The designations in the drawings have the following meanings:
1-impeller 2-driving part 3-shell 4-stator assembly 5-rotor assembly 6-water inlet 7-water outlet 8-guide vane 9A-outlet side sliding bearing 9B-inlet side sliding bearing 10-wear ring 11-impeller 12-water inlet 13-water outlet 14-upper circulation flow channel 15-lower circulation flow channel 16-massage hole 17-rectification grid
Detailed Description
The present invention will be described in detail with reference to the following examples.
Example 1
As shown in fig. 1-3, a borderless swimming pool comprises a pool body, wherein a pool pump 1 is arranged in the pool body, the pool pump comprises an impeller 11, and the impeller 11 is a small hub ratio impeller.
Example 2
As shown in fig. 1-3, on the basis of embodiment 1, it is preferable that the swimming pool body further includes a water inlet 12, a water outlet 13, an upper circulation flow channel 14, a lower circulation flow channel 15, a massage hole 16 and a rectification grid 17, wherein the massage hole 16 is communicated with the swimming pool pump 1 through the upper circulation flow channel 4, the water outlet 13 is communicated with the swimming pool pump 1 through the lower circulation flow channel 15, and the swimming pool pump 1 is further communicated with the water inlet 12.
Example 3
As shown in fig. 4, on the basis of embodiment 2, the pool pump further comprises a driving part 2 for driving a small hub to rotate than the impeller, the drainage pump further comprises a housing 3, the driving part 2 comprises a stator assembly 4 fixed on the housing 3, the driving part 2 further comprises a rotor assembly 5 matched with the stator assembly 4, the rim of the small hub is fixedly connected with the inner wall of the rotor assembly 4 and rotates along with the rotor assembly 4, and the small hub is hollow compared with the middle part of the impeller.
The utility model discloses a fluorine lining, including casing 3, rotor subassembly 5, stator module 4, water inlet 6, delivery port 7, rotor subassembly 5, water outlet 7, water inlet 6, delivery port 7 are equipped with respectively to the 3 both sides of casing, 5 both ends of rotor subassembly link to each other with water inlet 6, delivery port 7 respectively, delivery port 7 is equipped with the stator 8 with impeller 1 complex, the water wall of crossing of casing 3, rotor subassembly 5, stator module 4 all is equipped with the anticorrosive.
The rotor assembly 5 is located in the stator assembly 4 through the wear-resistant ring 10, the upper side and the lower side of the rotor assembly 5 are respectively provided with an outlet side sliding bearing 9A facilitating the matching and rotation of the rotor assembly 5 and the water outlet 7 and an inlet side sliding bearing 9B facilitating the matching and rotation of the rotor assembly 5 and the water inlet 6, a cooling channel for cooling and lubrication is formed by the surrounding among the rotor assembly 5, the water outlet 7, the stator assembly 4 and the water inlet 6, and an anti-corrosion lining layer adopting a fluorine lining process is arranged on the cooling channel.
Example 4
On the basis of any one of embodiments 1-3, the hydraulic design parameters of the small hub ratio impeller design of a certain water discharge pump are as follows: head H2 m, flow Q270 m3H, the motor speed n is 1450r/min, the specific speed ns＝862。
S1, obtaining the outer diameter D of the impeller with the small hub ratio;
s11, obtaining the estimated value D of the outer diameter of the impeller with the small hub ratio by the following formulaEstimated value,
Estimated outer diameter D of impellerEstimated valueTaking the integer of 188mm as the reference,
s12, obtaining the small hub ratio impeller hub diameter d through the following formula,
d＝Rd*Destimated value＝37.6mm
The hub diameter d is 38mm in integer.
S13, obtaining the actual value D of the outer diameter of the impeller with the small hub ratio by the following formula,
the actual value D of the outer diameter of the impeller with small hub ratio is 164mm in integer
Checking the external dimension of the impeller by the following formula:
d is 164mmh38mm as the basic dimensional parameter of the drain pump, in which case Rd＝dh/D20.232, between 0.1 and 0.3, falls within the range of small hub ratios.
S2, determining the number of blades and the blade airfoil of the impeller with the small hub ratio;
the phenomenon of squeezing fluid by the blades at the hub is obviously aggravated by the excessive number of the blades of the impeller with small hub ratio, the number of the blades is determined to be 3-5, and the blade is rotated with the specific speed nsIs increased and decreased. The specific speed n of the pump of the embodimentsAnd the number of blades belongs to an intermediate specific speed interval, so that 4 blades are counted, and the blade airfoil adopts an NACA4406 series airfoil.
S3, obtaining the blade cascade density S at the edge of the impeller with small hub ratioyAnd blade row density s at the hubg；
S31, obtaining the density S of the blade cascade at the wheel edge through the following formulay，
sy＝6.1751k+0.01254
Wherein,
k＝-5.0162×10-11×ns 3+3.04657×10-7×ns 2-6.32312×10-4×ns+0.4808
through calculation, sy＝0.8153，
When a small-hub impeller is designed by using a traditional design method, the impeller is seriously twisted near the hub, the chord length is too small, and even the situation that the direction of the fluid flowing out of the hub is opposite to the main flow direction occurs, so that the blade cannot be designed. Therefore, the conventional calculation formula needs to be corrected. The general correction strategy is to increase the chord length of the impeller near the hub, increase the density of the blade cascade at the hub by a proper amount and increase the outlet lift near the hub under the condition of not causing too serious displacement.
S32, obtaining the blade cascade density S at the hub through the following formulag，
sg＝(1.7～2.1)sy
Wherein s isgWhen the specific rotating speed is high, the value is large,
for the present embodiment, sg＝1.7sy，sg＝1.3859。
The density of the blade cascade at other positions is uniformly increased from the wheel rim to the wheel hub according to a linear change rule.
S4, dividing blades of the impeller with the small hub ratio into m cylindrical sections in an equidistant mode, sequentially marking the cylindrical sections as 1-1, 2-2, … … and m-m from the hub to the edge, and respectively obtaining an airfoil arrangement angle beta of each cylindrical sectionL；
S41, obtaining the inlet setting angle beta of each cylindrical section through the following formula1And outlet setting angle beta2，
Wherein is beta'1Is an inlet liquid flow angle and is characterized in that,
u is the peripheral speed, vmIs the flow velocity of the axial surface of the inlet of the blade,
is the coefficient of blade displacement, pi is the circumferential ratio, etavFor pump volumetric efficiency, D is the outer diameter of the impeller with small hub ratio, D is the hub diameter of the impeller with small hub ratio; delta beta1Is an entrance attack angle; beta'2Is the angle of the liquid flow at the outlet,
vu2being the component of the absolute velocity in the circumferential direction,
ηhthe hydraulic efficiency of the pump is shown, xi is a correction coefficient, g is the gravity acceleration, and H is the lift; delta beta2An exit attack angle;
s42, obtaining the airfoil arrangement angle beta of each cylindrical section through the following formulaL
βL＝(β1+β2)/2
The inlet seating angles β of the first to mth cylindrical sections are obtained by the formula in S411Is selected to be closest to the rim, and the cross-sectional diameters of the three cylindrical sections closest to the rim and the corresponding inlet seating angles beta are selected1Fitting the values of (a) to obtain the following quadratic polynomial:
y1＝a1x2+b1x+c1
wherein, y1Setting an angle beta for the inlet1X is the diameter of the cross section of the cylinder, a1、b1And c1Is a constant number of times, and is,
respectively substituting the diameters of the cross sections of the first to the mth cylindrical cross sections into the quadratic polynomial to obtain the corrected inlet placement angles beta of the first to the mth cylindrical cross sections1A value of (d);
the outlet setting angles β of the first to m-th cylindrical sections are obtained by the formula in S412Is selected to be closest to the rim, the cross-sectional diameter of the three cylindrical sections closest to the rim and the corresponding outlet seating angle beta2Fitting the values of (a) to obtain the following quadratic polynomial:
y2＝a2x2+b2x+c2
wherein, y2Setting an angle beta for the outlet2X is the diameter of the cross section of the cylinder, a2、b2And c2Is a constant number of times, and is,
respectively substituting the diameters of the first to the mth cylindrical sections into the quadratic polynomial to obtain the corrected outlet placement angles beta of the first to the mth cylindrical sections2The value of (a) is,
the corrected inlet placement angle β described above is substituted by the formula in S421And outlet setting angle beta2Obtaining a repairWing profile setting angle beta of each cylindrical section right behindLThe value of (c).
The value of m in this example is 7,
the inlet seating angle β of each cylindrical section is obtained by the formula in S411Wherein section 1-1 is 57.83, section 2-2 is 44.90, section 3-3 is 36.31, section 4-4 is 30.54, section 5-5 is 26.57, section 6-23.78, section 7-7 is 21.83;
selecting inlet placement angles beta of the sections 4-4, 5-5 and 6-61Is a dependent variable y, the section diameter of the corresponding section is an independent variable x, fitting is carried out to obtain the following formula,
y＝59.25-0.38x+0.00095x2
the inlet setting angle beta of each cylindrical section according to the formula1Correcting the value of (a) to obtain a corrected value, wherein the section 1-1 is 46.05, the section 2-2 is 39.93, the section 3-3 is 34.64, the section 4-4 is 30.19, the section 5-5 is 26.57, the section 6-6 is 23.78, and the section 7-7 is 21.83;
the outlet setting angle β of each cylindrical section is obtained by the formula in S412Wherein the section 1-1 is-46.56, the section 2-2 is-85.37, the section 3-3 is 61.96, the section 4-4 is-43.99, the section 5-5 is 34.14, the section 6-6 is 28.18, and the section 7-7 is 24.30;
selecting outlet placement angles beta of the sections 4-4, 5-5 and 6-62Is a dependent variable y, the section diameter of the corresponding section is an independent variable x, fitting is carried out to obtain the following formula,
y＝109.89-0.91x+0.0024x2
setting angle beta of outlet of each cylindrical section according to the formula2The value of (a) is corrected to obtain a corrected value, wherein the section 1-1 is 48.77, the section 2-2 is 64.49, the section 3-3 is 52.30, the section 4-4 is 42.18, the section 5-5 is 34.14, the section 6-6 is 28.18, and the section 7-7 is 24.30;
the corrected inlet placement angle β described above is substituted by the formula in S421And outlet setting angle beta2Obtaining corrected airfoil lay-up angles beta of the cylindrical sectionsLWherein the value of (1) is 62.41 for the section 1-1, 52.21 for the section 2-2, 43.37 for the section 3-3, 36.19 for the section 4-4, 30.36 for the section 5-5, 25.98 for the section 6-6, 23.07 for the section 7-7
S6, determining the blade thickness of the impeller with the small hub ratio;
the blade maximum thickness at the wheel edge is 10mm, and the blade maximum thickness at the wheel hub is 5mm, and the thickening is carried out according to the NACA4406 airfoil profile.
S7, verifying the method by adopting a Computational Fluid Dynamics (CFD) technology, and firstly, carrying out two-position design on the small hub ratio impeller hydraulic model designed according to the design method in a computer-aided design (CAD); secondly, guiding the designed hydraulic model into three-dimensional design software to generate a three-dimensional impeller entity (as shown in figure 6), and further processing on the basis to obtain a three-dimensional calculation water body; thirdly, the processed model is led into meshing software ANSYS ICEM for meshing; and finally, performing numerical simulation by using fluid mechanics analysis software ANSYS CFX or ANSYS FLUENT and the like, wherein the calculation method and the boundary condition are set as follows
The method is characterized in that a finite volume method is adopted to disperse a three-dimensional incompressible fluid control equation, and the control equation of three-dimensional turbulence numerical simulation comprises a cavitation model based on a two-phase flow mixing model, a Reynolds time average (RANS) Navier-Stokes (N-S) equation and an SST k-omega (shear stress transport) turbulence model more suitable for fluid separation. The control equation dispersion adopts a control volume method, an equation diffusion term is in a central difference format, and a convection term is in a second-order windward format. The equation solution adopts a separation semi-implicit pressure coupling algorithm. The inlet boundary condition adopts a total pressure inlet, the outlet boundary condition adopts a mass flow outlet, a wall function adopts a non-slip wall, the reference pressure is 0Pa, the energy transfer between a rotating part (impeller) and a static part (guide vane) is connected in a Frozen Rotor mode, and the calculation convergence standard is set as 10-5The medium is 25 degrees of water.
It should be noted that, when the small hub ratio impeller prepared by the preparation method of the present invention is applied to the drain pump of the present invention, the hub of the small hub ratio impeller should be removed (thereby achieving the effect of shaft-less drainage), and the rim of the small hub ratio impeller should be fixedly connected to the inner wall of the rotor assembly, as shown in fig. 11.
And (4) analyzing a calculation result:
fig. 7 shows a flow Q-lift H curve and a flow Q-efficiency η curve of a numerical simulation of an impeller with a small hub ratio, which can be obtained from the graph, and the lift of the pump is 2.05m under a design condition. The numerical simulation result and the design lift H are compareddesCompared with 2m, the error is 2.5%, and the error is within the allowable range of engineering error, and the accuracy of the design method is verified.
Fig. 8 is a velocity flow diagram of numerical simulation of an impeller with a small hub ratio, and it can be seen from the figure that the flow of fluid is relatively uniform before entering the impeller, the water continuously rotates to do work after passing through the impeller rotating at a high speed, and the flow of water shows a spiral motion near the outlet under the influence of the rotation of the impeller. In general, no obvious secondary reflux phenomenon exists, and the flowing effect of water is better.
Fig. 9 is a total pressure distribution diagram at the middle section of the impeller blade, and it can be seen from the diagram that under the influence of the rotation of the blade, a uniform low-pressure area appears at the inlet of the blade, and the pressure distribution at the outlet of the blade is relatively uniform.
In order to further verify the accuracy of the method, the numerical simulation result and the model experiment result are compared and analyzed. From fig. 10A, 10B, it can be derived that the experimental head H of the pump at the design operating pointexpThe numerical simulation result is compared with the model experiment with an error of 1.99 percent when the value is 2.01 m. The comparison of the efficiency curves can result in a numerical simulation efficiency of 84.5%, a model experiment efficiency of 80.7% and an error of only 4.7%. Therefore, the impeller obtained by the design method of the impeller with the small hub ratio can completely meet the design requirement, and meanwhile, the accuracy of the method is verified.
Although the present invention has been described in detail with reference to the foregoing embodiments, it will be apparent to those skilled in the art that changes may be made in the embodiments and/or equivalents thereof without departing from the spirit and scope of the invention. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (7)
1. A borderless swimming pool is characterized by comprising a swimming pool body, wherein a swimming pool pump (1) is arranged in the swimming pool body, the swimming pool pump comprises an impeller (11), and the impeller (11) is an impeller with a small hub ratio;
the design method of the impeller with the small hub ratio comprises the following steps:
s1, obtaining the outer diameter D of the impeller with the small hub ratio;
s2, determining the number of blades and the blade airfoil of the impeller with the small hub ratio;
s3, obtaining the blade cascade density S at the edge of the impeller with small hub ratioyAnd blade row density s at the hubg；
S4, dividing blades of the impeller with the small hub ratio into m cylindrical sections in an equidistant mode, sequentially marking the cylindrical sections as 1-1, 2-2, … … and m-m from the hub to the edge, and respectively obtaining an airfoil arrangement angle beta of each cylindrical sectionL；
S5 for airfoil setting angle beta in S4LCorrecting the value of (A);
s6, determining the blade thickness of the impeller with the small hub ratio;
s7, modeling parameters of the impeller with the small hub ratio obtained in the S1-S6, carrying out numerical simulation on the established impeller model to obtain a simulation lift value, and if the simulation lift value is within the range of the design lift value, completing the design of the impeller with the small hub ratio;
if the simulation lift value is out of the design lift value range, the simulation lift value is shifted to S1 for recalculation until the simulation lift value is in the design lift value range;
the specific steps of S1 include:
s11, obtaining the estimated value D of the outer diameter of the impeller with the small hub ratio by the following formulaEstimated value,
Wherein n is the motor rotation speed, pi is the circumference ratio, nsThe specific rotating speed of the rim driving pump, and H is the lift;
s12, obtaining the small hub ratio impeller hub diameter d through the following formula,
d＝Rd*Destimated value
Wherein R isdAs a hub ratio, DEstimated valueThe estimated value of the outer diameter of the small hub ratio impeller obtained in S11;
s13, obtaining the actual value D of the outer diameter of the impeller with the small hub ratio by the following formula,
wherein Q is flow, n is motor speed, pi is circumferential rate, and d is the diameter of the impeller hub with the small hub ratio obtained in S12;
the number of the blades in the S2 is 3-5, and the airfoil profile of each blade is an NACA series airfoil profile;
the actual value D of the small hub ratio impeller outer diameter obtained in S13 is checked by the following equation:
if D isCheckingWithin 0.1-0.3, is within the range of small hub ratios, if DCheckingOutside of 0.1 to 0.3, the actual value D of the outer diameter of the small hub ratio impeller is retrieved through S11 to S13.
2. A swimming pool without boundary as claimed in claim 1, wherein the swimming pool body is further provided with a water inlet (12), a water outlet (13), an upper circulation flow passage (14), a lower circulation flow passage (15), massage holes (16) and a flow-regulating fence (17), the massage holes (16) are communicated with the swimming pool pump (1) through the upper circulation flow passage (14), the water outlet (13) is communicated with the swimming pool pump (1) through the lower circulation flow passage (15), and the swimming pool pump (1) is further communicated with the water inlet (12).
3. A borderless swimming pool according to claim 1, wherein said pool pump further comprises a driving part (2) for driving the rotation of the small hub ratio impeller, said pool pump further comprises a housing (3), said driving part (2) comprises a stator assembly (4) fixed to the housing (3), said driving part (2) further comprises a rotor assembly (5) cooperating with the stator assembly (4), said small hub ratio impeller rim is fixedly connected to the inner wall of the rotor assembly (5) and follows the rotation of the rotor assembly (5), said small hub ratio impeller middle part is hollow;
a water inlet (6) and a water outlet (7) are respectively arranged on two sides of the shell (3), two ends of the rotor assembly (5) are respectively connected with the water inlet (6) and the water outlet (7), the water outlet (7) is provided with a guide vane (8) matched with the impeller (11), and the water passing wall surfaces of the shell (3), the rotor assembly (5) and the stator assembly (4) are respectively provided with an anti-corrosion lining layer adopting a fluorine lining process;
rotor subassembly (5) are located in stator module (4) through wear ring (10), just the upper and lower both sides of rotor subassembly (5) still are equipped with outlet side slide bearing (9A) and the inlet side slide bearing (9B) of being convenient for rotor subassembly (5) and delivery port (7) rotation of cooperateing respectively, enclose between rotor subassembly (5), delivery port (7), stator module (4) and water inlet (6) and enclose into the cooling channel who is used for cooling and lubrication, be equipped with the anticorrosive lining that adopts the fluorine lining technology on the cooling channel.
4. The borderless swimming pool of claim 1, wherein said specific step of S3 comprises:
s31, obtaining the density S of the blade cascade at the wheel edge through the following formulay，
sy＝6.1751k+0.01254
Wherein,
nsthe specific speed of the rim driven pump;
s32, obtaining the blade cascade density S at the hub through the following formulag，
sg＝(1.7～2.1)sy。
5. The borderless swimming pool of claim 1, wherein said specific step of S4 comprises:
s41, obtaining the inlet setting angle beta of each cylindrical section through the following formula1And outlet setting angle beta2，
Wherein is beta'1Is an inlet liquid flow angle and is characterized in that,
u is the peripheral speed, vmIs the flow velocity of the axial surface of the inlet of the blade,
is the coefficient of blade displacement, pi is the circumferential ratio, etavFor pump volumetric efficiency, D is the actual value of the outer diameter of the impeller with small hub ratio, D is the hub diameter of the impeller with small hub ratio; delta beta1Is an entrance attack angle; beta'2Is the angle of the liquid flow at the outlet,
vu2being the component of the absolute velocity in the circumferential direction,
ηhthe hydraulic efficiency of the pump is shown, xi is a correction coefficient, g is the gravity acceleration, and H is the lift; delta beta2An exit attack angle;
s42, obtaining the airfoil arrangement angle beta of each cylindrical section through the following formulaL，
βL＝(β1+β2)/2。
6. The borderless swimming pool according to claim 5, wherein the modification in S5 is performed as follows:
respectively obtaining the inlet setting angles beta of the m cylindrical sections through the formula in S411Is selected to be closest to the rim, and the cross-sectional diameters of the three cylindrical sections closest to the rim and the corresponding inlet seating angles beta are selected1Fitting the values of (a) to obtain the following quadratic polynomial:
y1＝a1x2+b1x+c1
wherein, y1Setting an angle beta for the inlet1X is the diameter of the cross section of the cylinder, a1、b1And c1Are all constant and are all provided with the same power,
respectively substituting the section diameters of the 1 st to the mth cylindrical sections into the quadratic polynomial to obtain the corrected inlet placement angles beta of the 1 st to the mth cylindrical sections1A value of (d);
the outlet setting angles beta of the m cylindrical sections are respectively obtained by the formula in S412Is selected to be closest to the rim, the cross-sectional diameter of the three cylindrical sections closest to the rim and the corresponding outlet seating angle beta2Fitting the values of (a) to obtain the following quadratic polynomial:
y2＝a2x2+b2x+c2
wherein, y2Setting an angle beta for the outlet2X is the diameter of the cross section of the cylinder, a2、b2And c2Are all constant and are all provided with the same power,
respectively substituting the section diameters of the 1 st to the mth cylindrical sections into the quadratic polynomial to obtain the outlet setting angles beta of the 1 st to the mth cylindrical sections after being corrected2The value of (a) is,
setting the corrected inlet setting angle beta1And a corrected outlet setting angle beta2Substituting the formula in S42 to obtain the corrected airfoil setting angle beta of each cylindrical sectionLThe value of (c).
7. The swimming pool without boundary of claim 1, wherein the thickness of the blade in S6 is smaller under the condition of satisfying the requirement of mechanical strength, and the thickness of the blade at the rim is 2 to 4 times of the thickness of the blade at the hub, and the thickness of the blade in the rest part is changed in a uniform and smooth transition way.
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| CN109800482B (en) * | 2018-12-29 | 2020-12-18 | 合肥工业大学 | Design method of impeller with small hub ratio |
| CN111270881A (en) * | 2020-02-07 | 2020-06-12 | 崔熙媛 | Mirror surface swimming pool system |
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| CN1037567A (en) * | 1989-04-07 | 1989-11-29 | 裴锺 | Axial-flow pipe pump |
| CN1084422C (en) * | 1995-12-31 | 2002-05-08 | 许青 | Counter-current swimming pool |
| US9038208B2 (en) * | 2006-12-20 | 2015-05-26 | Master Spas, Inc. | Swim spa with plenum arrangement at head end |
| CN204098548U (en) * | 2014-10-09 | 2015-01-14 | 孙荫模 | Short distance swimming training machine |
| CN205136044U (en) * | 2015-11-26 | 2016-04-06 | 江苏省水利勘测设计研究院有限公司 | Integral empty axle impeller pump of frequency conversion permanent magnet motor drive |
| CN107191385B (en) * | 2017-04-28 | 2023-12-01 | 合肥工业大学 | Magnetic driving type water jet propulsion pump |
| CN107386707A (en) * | 2017-09-18 | 2017-11-24 | 佛山市盈之创广告策划有限公司 | A kind of small-scale swimming pool |
| CN208105976U (en) * | 2017-12-29 | 2018-11-16 | 广州德诺泳池设备有限公司 | A kind of whole swimming pool with laminar flow propeller |
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