CN103758748B - The quaterfoil differential pump that a kind of sinusoidal non-circular gear drives - Google Patents

Abstract

The invention discloses the quaterfoil differential pump that a kind of sinusoidal non-circular gear drives.Power of the present invention is exported by motor, passes to input shaft through coupling; First sinusoidal non-circular gear and the second sinusoidal non-circular gear are all fixed on input shaft; First conjugation sinusoidal non-circular gear is fixed on output shaft, and engages with the first sinusoidal non-circular gear; Second conjugation sinusoidal non-circular gear and the second impeller are by axle sleeve consolidation, and axle sleeve kink is on output shaft; Second conjugation sinusoidal non-circular gear engages with the second sinusoidal non-circular gear; First impeller is fixed on output shaft; First impeller and the second impeller are provided with two panels blade, and all blade interior all install a unidirectional Decompression valves, and unidirectional Decompression valves direction is consistent with blade rotation direction.Discharge capacity of the present invention is large, stability of flow, and variable speed rule easily adjusts, and effectively solves traditional differential pump pressure pulsation and tired liquid problem.

Description

The quaterfoil differential pump that a kind of sinusoidal non-circular gear drives

Technical field

The invention belongs to displacement pump technical field, relate to blade differential pump, be specifically related to the quaterfoil differential pump that a kind of sinusoidal non-circular gear drives.

Background technique

The liquid pump that universal machine is conventional has reciprocating pump, plunger pump, diaphragm pump, roller pump and centrifugal pump, wherein: live (post) fills in pump higher outlet pressure, but require that the sealing between piston and cylinder barrel is reliable, and pressure surge is large; Diaphragm pump can produce a more stable liquid stream when multi-cylinder, but complex structure; Roller pump delivery is uniform when stabilization of speed, and along with the raising of pressure, leakage rate increases, the lifting rate of pump and the corresponding reduction of efficiency; Centrifugal pump structure is simple, easily manufactures, but its discharge capacity is large, and pressure is low, for the less demanding occasion of working pressure.There is respective defect in these pumps, can't meet the constant flow rate of part special mechanical requirement, the demand of high pressure well.

Existing differential pump mainly contains following several according to the difference of driving mechanism:

Rotating guide-bar-gear type blade differential pump, its drive system bears alternate load, produces gear tooth noise, and also can cause impact noise when each pair clearance is larger.

Universal-joint gear wheel mechanism drive vane differential pump, the input shaft of its universal joint mechanism and the angle of output shaft are the key parameters affecting pump performance.This angle is larger, and pump delivery is also larger, but along with the increase at this angle, the flow pulsation aggravation of pump and the transmission efficiency of universal joint reduce.

Distortion eccentric circle noncircular gear drive vane differential pump, its eccentric circle non-circular gear pitch curve adjustment parameter mainly eccentricity and deformation coefficient, adjustment amount is limited, Adjustment precision is not high, cause velocity ratio optimization, adjustment inconvenience, design dumb, be unfavorable for further optimal design, be difficult to optimize the problem such as pressure pulsation, tired liquid.Summary of the invention

The object of the invention is for the deficiencies in the prior art, the quaterfoil differential pump that a kind of sinusoidal non-circular gear drives be provided, this blade differential pump displacement is large, pressure is high, stability of flow, compact structure; The variable speed rule of driving mechanism easily adjusts, convenient function optimization; By installing unidirectional Decompression valves in blade, during pressure limit, getting through contiguous enclosed cavity, effectively solving existing differential pump and being stranded liquid problem.

The present invention includes driver part and differential pump parts.

Described driver part comprises driving gearbox, input shaft, output shaft, the first sinusoidal non-circular gear, the second sinusoidal non-circular gear, the first conjugation sinusoidal non-circular gear, the second conjugation sinusoidal non-circular gear and axle sleeve.Motor drives input shaft to rotate, and input shaft passes through two bearings in the two side of driving gearbox; The first described sinusoidal non-circular gear and the second sinusoidal non-circular gear are all fixedly mounted on input shaft; The two ends of output shaft are respectively by bearings on the tank wall of driving gearbox and pump case, and the first conjugation sinusoidal non-circular gear is fixedly mounted on output shaft, and engages with the first sinusoidal non-circular gear; Second conjugation sinusoidal non-circular gear and the second impeller are all cemented on axle sleeve, and axle sleeve kink is on output shaft; Second conjugation sinusoidal non-circular gear engages with the second sinusoidal non-circular gear;

Described differential pump parts comprise pump case, the first impeller, the second impeller and unidirectional Decompression valves; Described pump case along the circumferential direction offers the first liquid port, the first liquid sucting port, the second liquid port and the second liquid sucting port successively; First impeller is fixed on output shaft; The first described impeller and the second impeller are all symmetrically arranged with two panels blade; Along the circumferential direction, the blade of the first impeller and the alternate setting of blade of the second impeller; All blade interior all install a unidirectional Decompression valves.

According to pump structure, the centre distance initial value a of given first sinusoidal non-circular gear and the first conjugation sinusoidal non-circular gear ₀, then according to pitch curve sealing condition and meshing condition, adopt the search of advance and retreat method to obtain the exact value of centre distance a.Specifically be calculated as follows:

According to the relation of sinusoidal gear pair, the corner of the first sinusoidal non-circular gear with the corner of the first conjugation sinusoidal non-circular gear ₁meet relation:

Wherein, parameter n ₁be the exponent number of the first sinusoidal non-circular gear, value is 2; n ₂be the exponent number of the first conjugation sinusoidal non-circular gear, value is 2.

X ₁and y ₁meet relation:

Wherein, A is sinusoidal amplitude, and span is 0.001 ~ 0.01; Parameter sinusoidal periodic $l=\frac{2\mathrm{\π}\sqrt{{n_1}^2}+{n_2}^2}{n_1{n}_1};$

The pitch curve representation of the first sinusoidal non-circular gear is:

According to the noncircular gear theory of engagement, during the first sinusoidal non-circular gear rotating 360 degrees, the angular displacement of the first conjugation sinusoidal non-circular gear:

First sinusoidal non-circular gear and the first conjugation sinusoidal non-circular gear are second order noncircular gear, and therefore, during the first sinusoidal non-circular gear rotating 360 degrees, the first conjugation sinusoidal non-circular gear also rotating 360 degrees, can calculate the iterative of centre distance a:

Get centre distance initial value a ₀the search of advance and retreat method is adopted to calculate the exact value of centre distance a.

Described input shaft and output shaft are separately positioned on the two ends of gear-box; One end head of described input shaft is stretched out outside driving gearbox and is connected with motor by coupling.

The first described liquid port and the second liquid port are symmetrical arranged, and the first liquid sucting port and the second liquid sucting port are symmetrical arranged.

All unidirectional Decompression valves directions are consistent with blade rotation direction.

The first described sinusoidal non-circular gear and the structure of the second sinusoidal non-circular gear completely the same, the structure of the first conjugation sinusoidal non-circular gear and the second conjugation sinusoidal non-circular gear is completely the same, and the first sinusoidal non-circular gear, the second sinusoidal non-circular gear, the first conjugation sinusoidal non-circular gear and the second conjugation sinusoidal non-circular gear are second order noncircular gear; The initial installation phase difference of the initial installation phase difference of the first sinusoidal non-circular gear and the second sinusoidal non-circular gear, the first conjugation sinusoidal non-circular gear and the second conjugation sinusoidal non-circular gear is 90 °.

The velocity ratio of the first sinusoidal non-circular gear and the first conjugation sinusoidal non-circular gear is:

$i_{21}=\frac{\tan \left(\mathrm{\β}\right)+\mathrm{Ab}\cos \left({\mathrm{bx}}_1\right)}{1-\mathrm{Ab}\tan \left(\mathrm{\β}\right)\sin \left({\mathrm{bx}}_1\right)}$

The velocity ratio of the second sinusoidal non-circular gear and the second conjugation sinusoidal non-circular gear is:

$i_{43}=\frac{\tan \left(\mathrm{\β}\right)+\mathrm{Ab}\cos \left({\mathrm{bx}}_2\right)}{1-\mathrm{Ab}\tan \left(\mathrm{\β}\right)\sin \left({\mathrm{bx}}_2\right)}$

Wherein, θ is the initial installation phase difference of the first sinusoidal non-circular gear and the second sinusoidal non-circular gear, and value is 90 °.

Make the velocity ratio i of the first sinusoidal non-circular gear and the first conjugation sinusoidal non-circular gear ₂₁equal the velocity ratio i of the second sinusoidal non-circular gear and the second conjugation sinusoidal non-circular gear ₄₃, four different corners can be tried to achieve , corner get minimum value time, the angular displacement of the first sinusoidal non-circular gear is the angular displacement of the second sinusoidal non-circular gear is the corner of the first impeller and the second impeller is respectively:

The blade angle θ of the first impeller and the second impeller _leafvalue be 40 ° ~ 45 °; The equal and opposite in direction of the first liquid port, the first liquid sucting port, the second liquid port and the second liquid sucting port, and than the blade angle θ of blade _leaflittle 2 ~ 5 °.First liquid port centre bit angle setting of pump case first liquid sucting port centre bit angle setting second liquid port centre bit angle setting ψ _{row 2}=ψ _{row 1}+ π, the second liquid sucting port centre bit angle setting ψ _{inhale 2}=ψ _{inhale 1}+ π.

The minimum subtended angle of adjacent two blade now this enclosed cavity is minimum volume:

$V_{\min }=\frac{{\mathrm{\Δ\ψ}}_{\min }}{2}(R^2-r^2)\×h\×{10}^{-6}$

Wherein, R is blade radius, and r is impeller shaft radius, and h is vane thickness.

The maximum subtended angle of adjacent two blade now this enclosed cavity is maximum volume $V_{\min }=\frac{{\mathrm{\Δ\ψ}}_{\min }}{2}(R^2-r^2)\×h\×{10}^{-6}.$

The discharge capacity account representation of quaterfoil differential pump:

Q＝4×(V _max-V _min)＝2(Δψ _max-Δψ _min)(R ²-r ²)×h×10 _-6

The instantaneous flow calculation expression formula of quaterfoil differential pump:

$q=\frac{\mathrm{dV}}{\mathrm{dt}}=2h(R^2-r^2)|\frac{{\mathrm{d\ψ}}_1}{\mathrm{dt}}-\frac{{\mathrm{d\ψ}}_2}{\mathrm{dt}}|=2\mathrm{h\ω}(R^2-r^2)|i_{21}-i_{43}|$

Wherein, V is exhaust chamber volume; ω is the angular velocity of the first sinusoidal non-circular gear and the second sinusoidal non-circular gear, and its calculating formula is

The minimum volume of quaterfoil differential pump, maximum volume are stranded hydraulic coupling change calculations representation:

$\frac{{\mathrm{dp}}_1}{\mathrm{dt}}=\frac{K}{V_{\min }}\×q=\frac{K}{{\mathrm{\Δ\ψ}}_{\min }(R^2-r^2)}\×2\mathrm{h\ω}(R^2-r^2)|i_{21}-i_{43}|$

$\frac{{\mathrm{dp}}_2}{\mathrm{dt}}=\frac{K}{V_{\min }}\×q=\frac{K}{{\mathrm{\Δ\ψ}}_{\min }(R^2-r^2)}\×2\mathrm{h\ω}(R^2-r^2)|i_{21}-i_{43}|$

Wherein K is the Young's modulus of liquid.

The beneficial effect that the present invention has is:

The present invention adopts sinusoidal non-circular gear mechanism, sinusoidal non-circular gear pitch curve has six to adjust parameter, compare existing distortion eccentric circle noncircular gear adjustable parameter many, therefore sinusoidal non-circular gear variable speed transmission rule easily adjusts, and easily realizes the optimization of the performances such as differential pump delivery, pressure, flow.By installing unidirectional Decompression valves in blade, during pressure limit, getting through contiguous enclosed cavity, effectively solving existing differential pump and being stranded liquid problem.The differential pump liquid sucting port driven due to sinusoidal non-circular gear mechanism and liquid port symmetry, radial equilibrium is good, and non-constant speed drive is rotary motion, and reliable, the radial work loads that therefore operates steadily balance, pulsation controllability are good; Blade is many, discharge capacity is large, and simply, volumetric efficiency is high for the internal surface of pump case and blade shape.

Core institution of the present invention is two install the sinusoidal non-circular gear of phase place to difference, and parts are few, compact structure.Accompanying drawing explanation

Fig. 1 is kinematic sketch of mechanism of the present invention;

Fig. 2 is the overall structure sectional view of differential pump parts in the present invention;

Fig. 3 is the meshing relation schematic diagram of sinusoidal non-circular gear pitch curve when initial makeup location in the present invention;

Fig. 4 is blade limit position schematic diagram of the present invention;

Fig. 5 is instantaneous flow figure of the present invention.

In figure: 1, driving gearbox, 2, input shaft, 3, output shaft, 4, the first sinusoidal non-circular gear, the 5, second sinusoidal non-circular gear, the 6, first conjugation sinusoidal non-circular gear, 7, the second conjugation sinusoidal non-circular gear, 8, axle sleeve, 9, coupling, 10, motor, 11, pump case, 11-1, the first liquid port, 11-2, the first liquid sucting port, 11-3, the second liquid port, 11-4, the second liquid sucting port, 12, the first impeller, the 13, second impeller, 14, unidirectional Decompression valves.

Embodiment

Below in conjunction with drawings and Examples, the invention will be further described.

As illustrated in fig. 1 and 2, the quaterfoil differential pump that a kind of sinusoidal non-circular gear drives comprises driver part and differential pump parts.

Driver part comprises driving gearbox 1, input shaft 2, output shaft 3, first sinusoidal non-circular gear 4, second sinusoidal non-circular gear 5, first conjugation sinusoidal non-circular gear 6, second conjugation sinusoidal non-circular gear 7 and axle sleeve 8.Power is passed to input shaft 2 through coupling 9 by motor 10, and input shaft 2 passes through two bearings in the two side of driving gearbox 1; First sinusoidal non-circular gear 4 and the second sinusoidal non-circular gear 5 are all fixedly mounted on input shaft 2; The two ends of output shaft 3 are respectively by bearings on the tank wall of driving gearbox 1 and pump case 11, and the first conjugation sinusoidal non-circular gear 6 is fixedly mounted on output shaft 3, and engages with the first sinusoidal non-circular gear 4; Second conjugation sinusoidal non-circular gear 7 and the second impeller 13 are all cemented on axle sleeve 8, and axle sleeve 8 kink is on output shaft 3; Second conjugation sinusoidal non-circular gear 7 engages with the second sinusoidal non-circular gear 5;

Differential pump parts comprise pump case 11, first impeller 12, second impeller 13 and unidirectional Decompression valves 14; Pump case 11 along the circumferential direction offers the first liquid port 11-1, the first liquid sucting port 11-2, the second liquid port 11-3 and the second liquid sucting port 11-4 successively; First liquid port 11-1 and the second liquid port 11-3 is symmetrical arranged, and the first liquid sucting port 11-2 and the second liquid sucting port 11-4 is symmetrical arranged; First impeller 12 is fixed on output shaft 3; First impeller 12 and the second impeller 13 are all symmetrically arranged with two panels blade; Along the circumferential direction, the blade of the first impeller 12 and the alternate setting of blade of the second impeller 13; All blade interior all install a unidirectional Decompression valves 14, and unidirectional Decompression valves 14 direction is consistent with blade rotation direction.

As shown in Figure 3, the structure of the first sinusoidal non-circular gear 4 and the second sinusoidal non-circular gear 5 is completely the same, the structure of the first conjugation sinusoidal non-circular gear 6 and the second conjugation sinusoidal non-circular gear 7 is completely the same, and the first sinusoidal non-circular gear 4, second sinusoidal non-circular gear 5, first conjugation sinusoidal non-circular gear 6 and the second conjugation sinusoidal non-circular gear 7 are second order noncircular gear; The initial installation phase angle of the first sinusoidal non-circular gear 4 is θ ₁, the initial installation phase angle of the second sinusoidal non-circular gear 5 is θ ₂; The initial installation phase difference of the first sinusoidal non-circular gear 4 and the second sinusoidal non-circular gear 5, first conjugation sinusoidal non-circular gear 6 and the second conjugation sinusoidal non-circular gear 7 is θ ₁-θ ₂its value is 90 °, and the differential realizing the first impeller 12 and the second impeller 13 rotates, and makes the volume cyclically-varying of differential pump enclosed cavity, produce discharge opeing at the first liquid port 11-1 and the second liquid port 11-3, produce imbibition at the first liquid sucting port 11-2 and the second liquid sucting port 11-4.Because the non-at the uniform velocity transmission of sinusoidal non-circular gear is continuous print, enclosed cavity be in complete airtight time, blade still has differential to rotate, and this will make enclosed cavity pressure exceed limit value, and vicinity enclosed cavity is got through pressure release by unidirectional Decompression valves 14, prevents tired liquid.

The working principle of the quaterfoil differential pump that this sinusoidal non-circular gear drives:

Power is passed to the first sinusoidal non-circular gear 4 and the second sinusoidal non-circular gear 5 by coupling 9 and input shaft 2 by motor 10.First sinusoidal non-circular gear 4 engages with the first conjugation sinusoidal non-circular gear 6, second sinusoidal non-circular gear 5 engages with the second conjugation sinusoidal non-circular gear 7, power is passed to the first impeller 12, second conjugation sinusoidal non-circular gear 7 by output shaft 3 and power is passed to the second impeller 13 by axle sleeve 8 by the first conjugation sinusoidal non-circular gear 6.The installation phase place of two offset of sinusoidal noncircular gear pairs is different, and the differential realizing the first impeller 12 and the second impeller 13 rotates, thus realizes imbibition and discharge opeing.

According to pump structure, the centre distance initial value a of given first sinusoidal non-circular gear 4 and the first conjugation sinusoidal non-circular gear 6 ₀, then according to pitch curve sealing condition and meshing condition, adopt the search of advance and retreat method to obtain the exact value of centre distance a.Specifically be calculated as follows:

According to the relation of sinusoidal gear pair, the corner of the first sinusoidal non-circular gear 4 with the corner of the first conjugation sinusoidal non-circular gear 6 ₁meet relation:

Wherein, parameter n ₁be the exponent number of the first sinusoidal non-circular gear, value is 2; n ₂be the exponent number of the first conjugation sinusoidal non-circular gear, value is 2.

X ₁and y ₁meet relation:

Wherein, A is sinusoidal amplitude, and value is 0.004; Parameter sinusoidal periodic

$l=\frac{2\mathrm{\π}\sqrt{{n_1}^2}+{n_2}^2}{n_1{n}_1};$

The pitch curve representation of the first sinusoidal non-circular gear 4 is:

According to the noncircular gear theory of engagement, during the first sinusoidal non-circular gear 4 rotating 360 degrees, the angular displacement of the first conjugation sinusoidal non-circular gear 6:

First sinusoidal non-circular gear 4 and the first conjugation sinusoidal non-circular gear 6 are second order noncircular gear, and therefore, during the first sinusoidal non-circular gear 4 rotating 360 degrees, the first conjugation sinusoidal non-circular gear 6 also rotating 360 degrees, can calculate the iterative of centre distance a:

Get centre distance initial value a ₀=120mm, the exact value adopting the search of advance and retreat method to calculate centre distance a is 123.7mm.

After trying to achieve the exact value of centre distance a, can solve the row of pump case, liquid sucting port central position, quaterfoil differential pump delivery, instantaneous flow and minimum volume, maximum volume are stranded hydraulic coupling change representation.Specifically be calculated as follows:

The velocity ratio of the first sinusoidal non-circular gear 4 and the first conjugation sinusoidal non-circular gear 6 is:

$i_{21}=\frac{\tan \left(\mathrm{\β}\right)+\mathrm{Ab}\cos \left({\mathrm{bx}}_1\right)}{1-\mathrm{Ab}\tan \left(\mathrm{\β}\right)\sin \left({\mathrm{bx}}_1\right)}$

The velocity ratio of the second sinusoidal non-circular gear 5 and the second conjugation sinusoidal non-circular gear 7 is:

$i_{43}=\frac{\tan \left(\mathrm{\β}\right)+\mathrm{Ab}\cos \left({\mathrm{bx}}_2\right)}{1-\mathrm{Ab}\tan \left(\mathrm{\β}\right)\sin \left({\mathrm{bx}}_2\right)}$

Wherein, θ is the initial installation phase difference of the first sinusoidal non-circular gear 4 and the second sinusoidal non-circular gear 5, and value is 90 °.

Make the velocity ratio i of the first sinusoidal non-circular gear 4 and the first conjugation sinusoidal non-circular gear 6 ₂₁equal the velocity ratio i of the second sinusoidal non-circular gear 5 and the second conjugation sinusoidal non-circular gear 7 ₄₃, four different corners can be tried to achieve , corner get minimum value _minwhen=75 °, the angular displacement of the first sinusoidal non-circular gear 4 is ₁=75 °, the angular displacement of the second sinusoidal non-circular gear 5 is ₂= 1+90 °=165 °, the corner of the first impeller 12 and the second impeller 13 is respectively:

As shown in Figure 4, the blade angle θ of the first impeller 12 and the second impeller 13 _leafvalue be 45 °; The size of the first liquid port, the first liquid sucting port, the second liquid port and the second liquid sucting port is all than the blade angle θ of blade _leaflittle 2 °.First liquid port centre bit angle setting of pump case first liquid sucting port centre bit angle setting , the second liquid port centre bit angle setting ψ _{row 2}=ψ _{row 1}+ 180 °=250.5 °, the second liquid sucting port centre bit angle setting ψ _{inhale 2}=ψ _{inhale 1}+ 180 °=340.5 °.

Adjacent two blade minimum subtended angle Δ ψ _min=(ψ ₂+ 180 °)-(ψ ₁+ θ _leaf), now this enclosed cavity is minimum volume:

$V_{\min }=\frac{{\mathrm{\Δ\ψ}}_{\min }}{2}(R^2-r^2)\×h\×{10}^{-6}$

Wherein, R is blade radius, and value is 90mm; R is impeller shaft radius, and value is 20mm; H is vane thickness, and value is 50mm.

Adjacent two blade maximum subtended angle Δ ψ _max=(ψ ₁+ 180 °)-(ψ ₂+ 90 ° of+θ _leaf), now this enclosed cavity is maximum volume $V_{\min }=\frac{{\mathrm{\Δ\ψ}}_{\min }}{2}(R^2-r^2)\×h\×{10}^{-6}.$

The discharge capacity account representation of quaterfoil differential pump:

Q＝4×(V _max-V _min)＝2(Δψ _max-Δψ _min)(R ²-r ²)×h×10 ^-6=3278.6ml

The instantaneous flow calculation expression formula of quaterfoil differential pump:

$q=\frac{\mathrm{dV}}{\mathrm{dt}}=2h(R^2-r^2)|\frac{{\mathrm{d\ψ}}_1}{\mathrm{dt}}-\frac{{\mathrm{d\ψ}}_2}{\mathrm{dt}}|=2\mathrm{h\ω}(R^2-r^2)|i_{21}-i_{43}|$

Wherein, V is exhaust chamber volume; ω is the angular velocity of the first sinusoidal non-circular gear 4 and the second sinusoidal non-circular gear 5, and its calculating formula is the plotted curve of instantaneous flow as shown in Figure 5.

The minimum volume of quaterfoil differential pump, maximum volume are stranded hydraulic coupling change calculations representation:

$\frac{{\mathrm{dp}}_1}{\mathrm{dt}}=\frac{K}{V_{\min }}\×q=\frac{K}{{\mathrm{\Δ\ψ}}_{\min }(R^2-r^2)}\×2\mathrm{h\ω}(R^2-r^2)|i_{21}-i_{43}|$

$\frac{{\mathrm{dp}}_2}{\mathrm{dt}}=\frac{K}{V_{\min }}\×q=\frac{K}{{\mathrm{\Δ\ψ}}_{\min }(R^2-r^2)}\×2\mathrm{h\ω}(R^2-r^2)|i_{21}-i_{43}|$

Wherein K is the Young's modulus of liquid.

Be stranded hydraulic coupling change by the minimum volume, the maximum volume that calculate quaterfoil differential pump, can be and select the unidirectional Decompression valves in blade to provide reference, be generally used for the CLV ceiling limit value determining unidirectional Decompression valves.

Claims (6)

1. a quaterfoil differential pump for sinusoidal non-circular gear driving, comprises driver part and differential pump parts, it is characterized in that:

Described driver part comprises driving gearbox, input shaft, output shaft, the first sinusoidal non-circular gear, the second sinusoidal non-circular gear, the first conjugation sinusoidal non-circular gear, the second conjugation sinusoidal non-circular gear and axle sleeve; Motor drives input shaft to rotate, and input shaft passes through two bearings in the two side of driving gearbox; The first described sinusoidal non-circular gear and the second sinusoidal non-circular gear are all fixedly mounted on input shaft; The two ends of output shaft are respectively by bearings on the tank wall of driving gearbox and pump case, and the first conjugation sinusoidal non-circular gear is fixedly mounted on output shaft, and engages with the first sinusoidal non-circular gear; Second conjugation sinusoidal non-circular gear and the second impeller are all cemented on axle sleeve, and axle sleeve kink is on output shaft; Second conjugation sinusoidal non-circular gear engages with the second sinusoidal non-circular gear;

Described differential pump parts comprise pump case, the first impeller, the second impeller and unidirectional Decompression valves; Described pump case along the circumferential direction offers the first liquid port, the first liquid sucting port, the second liquid port and the second liquid sucting port successively; First impeller is fixed on output shaft; The first described impeller and the second impeller are all symmetrically arranged with two panels blade; Along the circumferential direction, the blade of the first impeller and the alternate setting of blade of the second impeller; All blade interior all install a unidirectional Decompression valves;

According to pump structure, the centre distance initial value a of given first sinusoidal non-circular gear and the first conjugation sinusoidal non-circular gear ₀, then according to pitch curve sealing condition and meshing condition, adopt the search of advance and retreat method to obtain the exact value of centre distance a; Specifically be calculated as follows:

According to the relation of sinusoidal gear pair, the corner of the first sinusoidal non-circular gear with the corner of the first conjugation sinusoidal non-circular gear meet relation:

Wherein, parameter n ₁be the exponent number of the first sinusoidal non-circular gear, value is 2; n ₂be the exponent number of the first conjugation sinusoidal non-circular gear, value is 2;

X ₁and y ₁meet relation:

Wherein, A is sinusoidal amplitude, and span is 0.001 ~ 0.01; Parameter sinusoidal periodic $l=\frac{2\mathrm{\π}\sqrt{{n_1}^2+{n_2}^2}}{n_1{n}_2};$

The pitch curve representation of the first sinusoidal non-circular gear is:

According to the noncircular gear theory of engagement, during the first sinusoidal non-circular gear rotating 360 degrees, the angular displacement of the first conjugation sinusoidal non-circular gear:

First sinusoidal non-circular gear and the first conjugation sinusoidal non-circular gear are second order noncircular gear, and therefore, during the first sinusoidal non-circular gear rotating 360 degrees, the first conjugation sinusoidal non-circular gear also rotating 360 degrees, can calculate the iterative of centre distance a:

Get centre distance initial value a ₀the search of advance and retreat method is adopted to calculate the exact value of centre distance a.

2. the quaterfoil differential pump of a kind of sinusoidal non-circular gear driving according to claim 1, is characterized in that: described input shaft and output shaft are separately positioned on the two ends of driving gearbox; One end head of described input shaft is stretched out outside driving gearbox and is connected with motor by coupling.

3. the quaterfoil differential pump of a kind of sinusoidal non-circular gear driving according to claim 1, it is characterized in that: the first described liquid port and the second liquid port are symmetrical arranged, the first liquid sucting port and the second liquid sucting port are symmetrical arranged.

4. the quaterfoil differential pump of a kind of sinusoidal non-circular gear driving according to claim 1, is characterized in that: all unidirectional Decompression valves directions are consistent with blade rotation direction.

5. the quaterfoil differential pump of a kind of sinusoidal non-circular gear driving according to claim 1, it is characterized in that: the first described sinusoidal non-circular gear and the structure of the second sinusoidal non-circular gear completely the same, the structure of the first conjugation sinusoidal non-circular gear and the second conjugation sinusoidal non-circular gear is completely the same, and the first sinusoidal non-circular gear, the second sinusoidal non-circular gear, the first conjugation sinusoidal non-circular gear and the second conjugation sinusoidal non-circular gear are second order noncircular gear; The initial installation phase difference of the initial installation phase difference of the first sinusoidal non-circular gear and the second sinusoidal non-circular gear, the first conjugation sinusoidal non-circular gear and the second conjugation sinusoidal non-circular gear is 90 °.

6. the quaterfoil differential pump of a kind of sinusoidal non-circular gear driving according to claim 1, is characterized in that: the velocity ratio of the first sinusoidal non-circular gear and the first conjugation sinusoidal non-circular gear is:

$i_{21}=\frac{tan\left(\mathrm{\β}\right)+Abcos\left({\mathrm{bx}}_1\right)}{1-Abtan\left(\mathrm{\β}\right)sin\left({\mathrm{bx}}_1\right)}$

The velocity ratio of the second sinusoidal non-circular gear and the second conjugation sinusoidal non-circular gear is:

$i_{43}=\frac{tan\left(\mathrm{\β}\right)+Abcos\left({\mathrm{bx}}_2\right)}{1-Abtan\left(\mathrm{\β}\right)sin\left({\mathrm{bx}}_2\right)}$

Wherein, θ is the initial installation phase difference of the first sinusoidal non-circular gear and the second sinusoidal non-circular gear, and value is 90 °;

Make the velocity ratio i of the first sinusoidal non-circular gear and the first conjugation sinusoidal non-circular gear ₂₁equal the velocity ratio i of the second sinusoidal non-circular gear and the second conjugation sinusoidal non-circular gear ₄₃, four different corners can be tried to achieve corner get minimum value time, the angular displacement of the first sinusoidal non-circular gear is the angular displacement of the second sinusoidal non-circular gear is the corner of the first impeller and the second impeller is respectively:

The blade angle θ of the first impeller and the second impeller _leafvalue be 40 ° ~ 45 °; The equal and opposite in direction of the first liquid port, the first liquid sucting port, the second liquid port and the second liquid sucting port, and the blade angle θ of ratio the first impeller and the second impeller _leaflittle 2 ~ 5 °; First liquid port centre bit angle setting of pump case first liquid sucting port centre bit angle setting second liquid port centre bit angle setting ψ _{row 2}=ψ _{row 1}+ π, the second liquid sucting port centre bit angle setting ψ _{inhale 2}=ψ _{inhale 1}+ π;

The minimum subtended angle of adjacent two blade now this enclosed cavity is minimum volume:

$V_{\min }=\frac{{\mathrm{\Δ\ψ}}_{\min }}{2}(R^2-r^2)\×h\×{10}^{-6}$

Wherein, R is blade radius, and r is impeller shaft radius, and h is vane thickness;

The maximum subtended angle of adjacent two blade now this enclosed cavity is maximum volume $V_{max}=\frac{{\mathrm{\Δ\ψ}}_{max}}{2}(R^2-r^2)\×h\×{10}^{-6};$

The discharge capacity account representation of quaterfoil differential pump:

Q＝4×(V _max-V _min)＝2(Δψ _max-Δψ _min)(R ²-r ²)×h×10 ^-6

The instantaneous flow calculation expression formula of quaterfoil differential pump:

$q=\frac{dV}{dt}=2h(R^2-r^2)\left|\frac{{\mathrm{d\ψ}}_1}{dt}-\frac{{\mathrm{d\ψ}}_2}{dt}\right|=2h\mathrm{\ω}(R^2-r^2)\left|i_{21}-i_{43}\right|$

Wherein, V is exhaust chamber volume; ω is the angular velocity of the first sinusoidal non-circular gear and the second sinusoidal non-circular gear, and its calculating formula is

The minimum volume of quaterfoil differential pump, maximum volume are stranded hydraulic coupling change calculations representation:

$\frac{{\mathrm{dp}}_1}{dt}=\frac{K}{V_{\min }}\×q=\frac{K}{{\mathrm{\Δ\ψ}}_{\min }(R^2-r^2)}\×2h\mathrm{\ω}(R^2-r^2)\left|i_{21}-i_{43}\right|$

$\frac{{\mathrm{dp}}_2}{dt}=\frac{K}{V_{max}}\×q=\frac{K}{{\mathrm{\Δ\ψ}}_{max}(R^2-r^2)}\×2h\mathrm{\ω}(R^2-r^2)\left|i_{21}-i_{43}\right|$

Wherein K is the Young's modulus of liquid.