Pin-type double-acting vane pump structure and control method for improving lubrication characteristics

Abstract

The present application discloses a pin-type double-acting vane pump structure and control method for improving lubrication characteristics, wherein the pin-type root chamber and the high-pressure chamber of the rear distribution plate are connected through an electromagnetic inverse proportional pressure reducing valve. The pin-type double-acting vane pump has a compact structure and does not affect the original working mode. It can adjust the oil pressure of the root chamber in real time according to information such as oil temperature, load pressure, and speed by controlling the electromagnetic inverse proportional pressure reducing valve, so that the oil film thickness between the blade tip and the inner curved surface of the stator is kept in the optimal state, effectively reducing the friction and wear between the blade tip and the inner curved surface of the stator, and improving the service life and working efficiency of the vane pump under different working conditions.

Description

Technical Field

[0001] The present application relates to the technical field of hydraulic transmission, and in particular to a pin-type double-acting vane pump structure and a control method for improving lubrication characteristics. Background Art

[0002] The pin-type double-acting vane pump is widely used in engineering machinery due to its high energy density and low noise. Its working mode includes: when the rotor rotates, the blades are pressed against the inner surface of the stator under the action of their own centrifugal force and the high-pressure oil at the bottom of the blades. As the stator curve changes, they make reciprocating motion in the blade groove. When the blades move from the small diameter to the large diameter, the volume between the two blades gradually increases, forming a local vacuum and absorbing oil. When the blades move from the large diameter to the small diameter, the volume between the two blades gradually decreases and discharges oil. The rotor rotates one circle, and the blades reciprocate twice in the groove, forming two oil suction and discharge. Among them, the lubrication characteristics between the top of the blade and the inner curved surface of the stator are the key factors affecting the working performance and service life of the vane pump. If the oil film thickness is too small, the friction and wear between the top of the blade and the stator will be aggravated, reducing the mechanical efficiency and the service life of the parts. If the oil film thickness is too large, the oil leakage at the top of the blade will increase and the volumetric efficiency will be reduced.

[0003] The existing pin-type double-acting vane pump design method can only make the pump have a higher working efficiency near the rated operating conditions. However, under different speeds, load pressures, and different oil temperatures, the oil film distribution between the blade tip and the inner curved surface of the stator changes significantly, which reduces the pump efficiency under non-rated conditions. Summary of the invention

[0004] The purpose of the present application is to provide a pin-type double-acting vane pump structure and control method with improved lubrication characteristics, which can improve the above-mentioned problems.

[0005] The embodiment of the present application is implemented as follows:

[0006] In a first aspect, the present application provides a pin-type double-acting vane pump structure with improved lubrication properties, comprising:

[0007] An electromagnetic inverse proportional pressure reducing valve and a front distribution plate, a rotating assembly and a rear distribution plate which are stacked in sequence;

[0008] The rotating assembly includes an annular stator, a rotor and a motor; the rotor is driven by the rotating shaft of the motor to rotate around the rotor center inside the annular shape of the annular stator;

[0009] The rotor is provided with an equal number of pin grooves and blade grooves that are interconnected, a pin is provided in the pin groove, a blade is provided in the blade groove, and the rotor cross section is centrally symmetrical about the center of the rotor; when the rotor rotates, the blade is pressed against the inner ring surface of the annular stator under the action of the high-pressure oil in the cavity at the root of the pin groove;

[0010] The root cavity of the pin slot is connected to the high-pressure cavity of the rear distribution plate through the electromagnetic inverse proportional pressure reducing valve, and the electromagnetic inverse proportional pressure reducing valve is used to adjust the oil pressure of the root cavity.

[0011] It can be understood that the present application discloses a pin-type double-acting vane pump structure with improved lubrication characteristics, and the root chamber of the pin slot is connected to the high-pressure chamber of the rear distribution plate through an electromagnetic inverse proportional pressure reducing valve. The design is compact and does not affect the original working mode. In addition, the oil pressure in the root chamber can be adjusted in real time according to information such as oil temperature, load pressure, and speed by controlling the electromagnetic inverse proportional pressure reducing valve, so that the oil film thickness between the blade tip and the inner curved surface of the stator is kept in the optimal state, effectively reducing the friction and wear between the blade tip and the inner curved surface of the stator, and improving the service life and working efficiency of the vane pump under different working conditions.

[0012] In an optional embodiment of the present application, the rotor is provided with at least one guide hole connected to the root cavity of the pin groove; the rear distribution plate is provided with a U-shaped groove connected to the guide hole; the oil inlet of the electromagnetic inverse proportional pressure reducing valve is connected to the high-pressure chamber on the rear distribution plate, and the oil outlet of the electromagnetic inverse proportional pressure reducing valve is connected to the U-shaped groove on the rear distribution plate.

[0013] In a second aspect, the present application provides a pin-type double-acting vane pump control system with improved lubrication characteristics, comprising an oil tank, a pin-type double-acting vane pump structure as described in any one of the first aspects, a controller, and a speed sensor, a thermometer, and a pressure sensor electrically connected to the controller; the controller is also electrically connected to the electromagnetic inverse proportional pressure reducing valve;

[0014] The speed sensor is arranged on the rotating shaft of the motor and is used to detect the rotation speed of the rotor; the oil suction port of the pin-type double-acting vane pump structure is connected to the oil tank, and the oil outlet of the pin-type double-acting vane pump structure is connected to the external load system through an oil pipe; the thermometer and the pressure sensor are arranged on the oil pipe, the thermometer is used to detect the oil temperature in the oil pipe, and the pressure sensor is used to detect the oil pressure in the oil pipe.

[0015] It can be understood that the present application discloses a pin-type double-acting vane pump control system for improving lubrication characteristics, including a pin-type double-acting vane pump structure and a speed sensor, a thermometer, and a pressure sensor for detecting rotor speed, oil temperature, and load pressure. The controller receives the rotor speed feedback from the speed sensor, the oil temperature feedback from the thermometer, and the load pressure feedback from the pressure sensor respectively; calculates the target pressure range of the pin groove root cavity when the minimum oil film thickness between the blade and the inner ring surface of the annular stator reaches the target thickness range; and controls the electromagnetic inverse proportional pressure reducing valve to adjust the cavity pressure of the pin groove root cavity to be within the target pressure range.

[0016] In a third aspect, the present application provides a control method for a pin-type double-acting vane pump with improved lubrication characteristics, which is applied to the controller of the pin-type double-acting vane pump control system disclosed in the second aspect, and comprises the following steps:

[0017] S1: establishing a calculation formula for the minimum oil film thickness between the blade and the inner ring surface of the annular stator according to an elastohydrodynamic lubrication model;

[0018] S2: Substituting the rotor speed fed back by the speed sensor and the oil temperature fed back by the thermometer into the calculation formula of the minimum oil film thickness, and substituting the oil pressure fed back by the pressure sensor as the load pressure into the calculation formula of the minimum oil film thickness, to obtain a relationship between the minimum oil film thickness and the pressure inside the cavity of the root of the pin groove;

[0019] S3: Calculating, according to the relationship, a target pressure range of the cavity pressure when the minimum oil film thickness reaches a target thickness range;

[0020] S4: Control the electromagnetic inverse proportional pressure reducing valve to adjust the internal pressure of the cavity at the root of the pin groove to be within the target pressure range.

[0021] It can be understood that the present application provides a control method for a pin-type double-acting vane pump with improved lubrication characteristics. The oil pressure in the root chamber can be adjusted in real time according to information such as oil temperature, load pressure, and speed by controlling the electromagnetic inverse proportional pressure reducing valve to optimize the distribution state of the friction pair oil film between the blade tip and the inner surface of the stator, so as to reduce the friction wear and oil leakage between the blade tip and the inner surface of the stator. Especially for electric engineering machinery, it is difficult for traditional pumps to maintain a high working efficiency outside the rated working point. The technical solution of the present application can improve the working efficiency and service life of the vane pump outside the rated working point, and adapt to the variable speed and variable load requirements in electric engineering machinery.

[0022] Among them, S1, S2, etc. are only step identifiers, and the execution order of the method is not necessarily in the order of numbers from small to large. For example, step S2 may be executed first and then step S1. This application does not impose any limitation on this.

[0023] In an optional embodiment of the present application, S1 includes:

[0024] S11: Calculating the equivalent radius of curvature R between the top of the blade and the inner ring surface of the annular stator according to the analysis of the pin-type double-acting vane pump structure;

[0025] S12: solving the contact pressure W between the blade tip and the inner ring surface of the annular stator according to the force balance equation;

[0026] S13: Substitute the equivalent curvature radius R and the contact pressure W into the following formula established according to the elastohydrodynamic lubrication model:

[0027]

[0028] Among them, h min represents the minimum oil film thickness between the blade and the inner ring surface of the annular stator; α represents the oil viscosity-pressure coefficient; represents the distance from the contact point between the blade tip and the annular stator to the center of the rotor; represents the angle of rotation of the rotating shaft; ω represents the rotor speed; R represents the equivalent radius of curvature; W represents the contact pressure; L represents the linear contact length between the tip of the blade and the inner surface of the annular stator;

[0029] E represents the equivalent elastic modulus between the blade and the annular stator, satisfying the following formula:

[0030]

[0031] Wherein, E1 and E2 represent the elastic modulus of blade and annular stator, respectively;

[0032] μ represents the current oil viscosity, which satisfies the following formula:

[0033]

[0034] Wherein, μ0 represents the viscosity of the oil at the initial temperature T0; P represents the load pressure, that is, the oil pressure in the oil pipe fed back by the pressure sensor; T represents the current oil temperature, that is, the oil temperature fed back by the thermometer;

[0035] S14: Obtain a calculation formula h for the minimum oil film thickness between the blade and the inner ring surface of the annular stator min =H(T,P,p d,ω). Wherein, H() represents the calculation function of the minimum oil film thickness, P represents the load pressure, p d Indicates the pressure inside the cavity at the root of the pin groove.

[0036] In an optional embodiment of the present application, the S11 includes:

[0037] The equivalent radius of curvature R between the blade tip and the inner ring surface of the annular stator is calculated according to the following formula:

[0038]

[0039] Wherein, r represents the fillet radius of the blade tip.

[0040] In an optional embodiment of the present application, the S12 includes:

[0041] The contact pressure W between the blade tip and the inner ring surface of the annular stator is solved according to the following force balance equation:

[0042]

[0043] Wherein, f1 represents the friction coefficient between the blade and the rotor; f2 represents the friction coefficient between the blade and the annular stator; N1 and N2 represent the contact force between the blade and the two sides of the blade slot respectively; γ represents the angle between the contact pressure W between the top of the blade and the inner ring surface of the annular stator and the radial direction of the blade; Fp1, Fp2 and Fp3 represent the oil pressure at the front side, rear side and top of the blade respectively; Fdv represents the oil pressure at the bottom of the blade; Fdp represents the oil pressure at the root of the pin slot, satisfying the following formula: F dp =πd 2 p d / 4; F cv represents the centrifugal force of the blade, and satisfies the following formula: Fcv=mvlcvω2, wherein mv represents the mass of the blade, lcv represents the distance between the blade and the center of the rotor, and ω represents the rotor speed; F cp The centrifugal force of the pin satisfies the following formula: F cp =m p l cp ω 2 , where mp represents the mass of the pin, lcp represents the distance between the pin and the center of the rotor; Fav represents the inertial force generated by the radial acceleration of the blade, satisfying the following formula: Fav=mvav, av represents the radial acceleration of the blade; Fap represents the inertial force generated by the radial acceleration of the pin, satisfying the following formula: Fap=mpap, ap represents the radial acceleration of the pin; F kvrepresents the Coriolis force of the blade, satisfying the following formula: F kv =2m v ωv v , v v represents the radial velocity of the blade; Fkp represents the Coriolis force of the pin, satisfying the following formula: F kp =2m p ωv p , v p represents the radial velocity of the pin; F vv represents the friction force between the blade and the blade slot; Fvp represents the friction force between the pin and the pin slot; l1, l2 and lp1 represent the force arms of N1, N2 and Fp1 respectively relative to the contact point between the blade and the inner surface of the annular stator; tv represents the blade thickness; Lv represents the blade height.

[0044] In an optional embodiment of the present application, the target thickness range is:

[0045]

[0046] Wherein, Ra1 represents the roughness of the blade tip, and Ra2 represents the roughness of the inner surface of the annular stator.

[0047] Beneficial effects:

[0048] The present application discloses a pin-type double-acting vane pump structure with improved lubrication characteristics, in which the root chamber of the pin slot is connected to the high-pressure chamber of the rear distribution plate through an electromagnetic inverse proportional pressure reducing valve. The design is compact and does not affect the original working mode. The oil pressure of the root chamber can be adjusted in real time according to information such as oil temperature, load pressure, and speed by controlling the electromagnetic inverse proportional pressure reducing valve, so that the oil film thickness between the blade tip and the inner curved surface of the stator is kept in the optimal state, effectively reducing the friction and wear between the blade tip and the inner curved surface of the stator, and improving the service life and working efficiency of the vane pump under different working conditions.

[0049] The present application discloses a pin-type double-acting vane pump control system for improving lubrication characteristics, including a pin-type double-acting vane pump structure and a speed sensor, a thermometer, and a pressure sensor for detecting rotor speed, oil temperature, and load pressure. The controller receives the rotor speed feedback from the speed sensor, the oil temperature feedback from the thermometer, and the load pressure feedback from the pressure sensor respectively; calculates the target pressure range of the pin-groove root cavity when the minimum oil film thickness between the blade and the inner ring surface of the annular stator reaches the target thickness range; controls the electromagnetic inverse proportional pressure reducing valve to adjust the cavity pressure of the pin-groove root cavity to be within the target pressure range, so that the oil film thickness between the blade tip and the stator inner curved surface remains in the optimal state.

[0050] The present application provides a control method for a pin-type double-acting vane pump that improves lubrication characteristics. The oil pressure in the root chamber can be adjusted in real time according to information such as oil temperature, load pressure, and speed by controlling the electromagnetic inverse proportional pressure reducing valve to optimize the distribution of the friction pair oil film between the blade tip and the inner surface of the stator, so as to reduce the friction wear and oil leakage between the blade tip and the inner surface of the stator. Especially for electric engineering machinery, it is difficult for traditional pumps to maintain a high working efficiency outside the rated working point. The technical solution of the present application can improve the working efficiency and service life of the vane pump outside the rated working point, and adapt to the variable speed and variable load requirements in electric engineering machinery.

[0051] In order to make the above-mentioned objects, features and advantages of the present application more obvious and understandable, optional embodiments are specifically listed below and described in detail with reference to the attached drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0052] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings required for use in the embodiments will be briefly introduced below. It should be understood that the following drawings only show certain embodiments of the present application and therefore should not be regarded as limiting the scope. For ordinary technicians in this field, other related drawings can be obtained based on these drawings without paying creative work.

[0053] Figure 1 The present application provides a pin-type double-acting vane pump control system with improved lubrication characteristics;

[0054] Figure 2 It is a structural schematic diagram of a pin-type double-acting vane pump with improved lubrication characteristics provided by the present application;

[0055] Figure 3 yes Figure 2 A cross-sectional view of a pin-type double-acting vane pump shown;

[0056] Figure 4 yes Figure 2 The structural schematic diagram of the rear distribution plate shown;

[0057] Figure 5 yes Figure 2 A cross-sectional view of a pin-type double-acting vane pump shown;

[0058] Figure 6 yes Figure 2 The schematic diagram of force analysis of the blades in the pin-type double-acting vane pump shown in FIG.

[0059] Figure 7 It is a comparison diagram of the film thickness ratio before and after the optimization of the pin-type double-acting vane pump control method provided by this application. DETAILED DESCRIPTION

[0060] The following will be combined with the drawings in the embodiments of the present application to clearly and completely describe the technical solutions in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of this application.

[0061] First, as Figures 1 to 4 As shown, the present application provides a pin-type double-acting vane pump structure 10 with improved lubrication characteristics, which includes an electromagnetic inverse proportional pressure reducing valve 1 and a front distribution plate 2, a rotating assembly 3 and a rear distribution plate 4 stacked in sequence.

[0062] The rotating assembly 3 includes an annular stator 31, a rotor 32 and a motor 33; the rotor 32 is driven by the rotating shaft 330 of the motor 33 to rotate around the rotor center in the annular interior of the annular stator 31. The rotor center is the geometric center of the rotor cross section, such as Figure 4 The cross section of the rotor shown is a circular turntable, and the center of the rotor is the center of the circular turntable.

[0063] The rotor 32 is provided with an equal number of pin grooves and blade grooves that are interconnected. A pin 321 is provided in the pin groove, and a blade 322 is provided in the blade groove. The cross section of the rotor 32 is a centrally symmetrical structure about the center of the rotor. When the rotor 32 rotates, the blade is pressed against the inner ring surface of the annular stator 31 under the action of the high-pressure oil in the cavity 34 at the root of the pin groove.

[0064] In the pin-type double-acting vane pump, the rotor 32 and the rear distribution plate 4 are stacked. When working, the rotor 32 rotates around the center of the rotor, and the blades 322 are thrown out by the centrifugal force and the high-pressure oil at the bottom of the blades 322, close to the inner surface of the stator 31, and reciprocate in the blade groove as the curve of the stator 31 changes. When the blade 322 moves from the small diameter to the large diameter, the volume between the two blades gradually increases, forming a local vacuum to absorb oil. When the blade 322 moves from the large diameter to the small diameter, the volume between the two blades gradually decreases and discharges oil. The rotor 32 rotates one circle, and the blade reciprocates twice in the groove, forming two times of oil suction and discharge.

[0065] like Figure 2 and Figure 3 As shown, the root cavity 34 of the pin groove is connected to the high-pressure cavity 41 of the rear distribution plate 4 through the electromagnetic inverse proportional pressure reducing valve 1, and the electromagnetic inverse proportional pressure reducing valve 1 is used to adjust the oil pressure of the root cavity.

[0066] It can be understood that the present application discloses a pin-type double-acting vane pump structure with improved lubrication characteristics, and the pin groove root chamber 34 is connected to the high-pressure chamber of the rear distribution plate 4 through the electromagnetic inverse proportional pressure reducing valve 1. The design structure is compact and does not affect the original working mode, and the oil pressure in the root chamber can be adjusted in real time according to information such as oil temperature, load pressure, and speed by controlling the electromagnetic inverse proportional pressure reducing valve 1, so that the oil film thickness between the blade tip and the inner curved surface of the stator is maintained in the optimal state, effectively reducing the friction and wear between the blade tip and the inner curved surface of the stator, and improving the service life and working efficiency of the vane pump under different working conditions.

[0067] In an optional embodiment of the present application, if Figure 2 and Figure 3 As shown, the rotor 32 is provided with at least one guide hole 35 connected to the cavity 34 at the root of the pin groove; the rear distribution plate 4 is provided with a U-shaped groove 36 connected to the guide hole 35; the oil inlet of the electromagnetic inverse proportional pressure reducing valve 1 is connected to the high-pressure chamber on the rear distribution plate 4, and the oil outlet of the electromagnetic inverse proportional pressure reducing valve 1 is connected to the U-shaped groove 36 on the rear distribution plate 4.

[0068] Second, as Figure 5 As shown, the present application provides a pin-type double-acting vane pump control system with improved lubrication characteristics, which includes an oil tank 20, a pin-type double-acting vane pump structure 10 as any one of the first aspects, a controller 60, and a speed sensor 30, a thermometer 40, and a pressure sensor 50 electrically connected to the controller; the controller is also electrically connected to the electromagnetic inverse proportional pressure reducing valve 1.

[0069] The speed sensor 30 is arranged on the rotating shaft 330 of the motor 33, and is used to detect the rotation speed of the rotor 32; the oil suction port of the pin-type double-acting vane pump structure is connected to the oil tank 20, and the oil outlet of the pin-type double-acting vane pump structure is connected to the external load system 100 through the oil pipe; the thermometer 40 and the pressure sensor 50 are arranged on the oil pipe, the thermometer 40 is used to detect the oil temperature in the oil pipe, and the pressure sensor 50 is used to detect the oil pressure in the oil pipe, and the oil pressure in the oil pipe is the load pressure of the pin-type double-acting vane pump structure 10.

[0070] In the embodiment of the present invention, the controller may be a central processing unit (CPU), and the controller may also be other general-purpose processors, digital signal processors (DSP), application-specific integrated circuits (ASIC), field-programmable gate arrays (FPGA) or other programmable logic devices, discrete gate or transistor logic devices, discrete hardware components, etc. A general-purpose processor may be a microprocessor or the processor may also be any conventional processor, etc.

[0071] It can be understood that the present application discloses a pin-type double-acting vane pump control system for improving lubrication characteristics, including a pin-type double-acting vane pump structure and a speed sensor 30, a thermometer 40, and a pressure sensor 50 for detecting the speed, oil temperature, and load pressure of the rotor 32. The controller receives the speed of the rotor 32 fed back by the speed sensor 30, the oil temperature fed back by the thermometer 40, and the load pressure fed back by the pressure sensor 50 respectively; calculates the target pressure range of the pin groove root cavity 34 when the minimum oil film thickness between the blade and the inner ring surface of the annular stator 31 reaches the target thickness range; and controls the electromagnetic inverse proportional pressure reducing valve 1 to adjust the cavity pressure of the pin groove root cavity 34 to be within the target pressure range.

[0072] In a third aspect, the present application provides a control method for a pin-type double-acting vane pump with improved lubrication characteristics, which is applied to a controller of the pin-type double-acting vane pump control system disclosed in the second aspect, and comprises the following steps:

[0073] S1: Based on the elastohydrodynamic lubrication model, a calculation formula for the minimum oil film thickness between the blade and the inner ring surface of the annular stator is established.

[0074] The calculation formula includes the relationship between the minimum oil film thickness and the rotor speed, oil temperature, and load pressure.

[0075] S2: Substitute the rotor speed fed back by the speed sensor and the oil temperature fed back by the thermometer into the calculation formula of the minimum oil film thickness, and substitute the oil pressure fed back by the pressure sensor as the load pressure into the calculation formula of the minimum oil film thickness to obtain the relationship between the minimum oil film thickness and the intracavity pressure of the pin groove root cavity.

[0076] S3: According to the relationship, the target pressure range of the cavity pressure when the minimum oil film thickness reaches the target thickness range is calculated.

[0077] In an optional embodiment of the present application, the target thickness range is:

[0078]

[0079] Among them, Ra1 represents the roughness of the blade tip, and Ra2 represents the roughness of the inner surface of the annular stator.

[0080] S4: Control the electromagnetic inverse proportional pressure reducing valve to adjust the internal pressure of the cavity at the root of the pin groove to be within the target pressure range.

[0081] Among them, S1, S2, etc. are only step identifiers, and the execution order of the method is not necessarily in the order of numbers from small to large. For example, step S2 may be executed first and then step S1. This application does not impose any limitation on this.

[0082] It can be understood that the present application provides a control method for a pin-type double-acting vane pump with improved lubrication characteristics. The oil pressure in the root chamber can be adjusted in real time according to information such as oil temperature, load pressure, and speed by controlling the electromagnetic inverse proportional pressure reducing valve to optimize the distribution state of the friction pair oil film between the blade tip and the inner surface of the stator, so as to reduce the friction wear and oil leakage between the blade tip and the inner surface of the stator. Especially for electric engineering machinery, it is difficult for traditional pumps to maintain a high working efficiency outside the rated working point. The technical solution of the present application can improve the working efficiency and service life of the vane pump outside the rated working point, and adapt to the variable speed and variable load requirements in electric engineering machinery.

[0083] In an optional embodiment of the present application, S1 includes:

[0084] S11: Based on the analysis of the pin-type double-acting vane pump structure, calculate the equivalent radius of curvature R between the vane tip and the inner ring surface of the annular stator.

[0085] Specifically, S11 includes:

[0086] According to the following formula, calculate the equivalent radius of curvature R between the blade tip and the inner ring surface of the annular stator:

[0087]

[0088] Where r is the radius of the blade tip fillet.

[0089] S12: The contact pressure W between the blade tip and the inner ring surface of the annular stator is solved according to the force balance equation.

[0090] Specifically, in an optional embodiment of the present application, S12 includes:

[0091] like Figure 6 Shown Figure 2The schematic diagram of the force analysis of the blades in the pin-type double-acting vane pump is shown in the figure. According to the following force balance equation, the contact pressure W between the blade tip and the inner ring surface of the annular stator is solved:

[0092]

[0093] Among them, f1 represents the friction coefficient between the blade and the rotor; f2 represents the friction coefficient between the blade and the annular stator; N1 and N2 represent the contact force between the blade and the two sides of the blade slot respectively; γ represents the angle between the contact pressure W between the top of the blade and the inner ring surface of the annular stator and the radial direction of the blade; Fp1, Fp2 and Fp3 represent the oil pressure at the front side, back side and top of the blade respectively; Fdv represents the oil pressure at the bottom of the blade; Fdp represents the oil pressure at the root of the pin slot, satisfying the following formula: F dp =πd 2 p d / 4; F p1 、F p2 and F p3 represents the oil pressure at the front side, rear side and top of the blade respectively; Fdv represents the oil pressure at the bottom of the blade; Fdp represents the oil pressure at the root of the pin groove, satisfying the following formula: dp =πd 2 p d / 4; F cv represents the centrifugal force of the blade, and satisfies the following formula: Fcv=mvlcvω2, wherein mv represents the mass of the blade, lcv represents the distance between the blade and the center of the rotor, and ω represents the rotor speed; F cp The centrifugal force of the pin satisfies the following formula: F cp =m p l cp ω 2 , where mp represents the mass of the pin, l cp represents the distance between the pin and the center of the rotor; Fav represents the inertial force of the blade caused by the radial motion acceleration, which satisfies the following formula: Fav = mvav, av represents the radial acceleration of the blade; Fap represents the inertial force of the pin caused by the radial motion acceleration, which satisfies the following formula: Fap = mpap, ap represents the radial acceleration of the pin; Fkv represents the Coriolis force of the blade, which satisfies the following formula: F kv =2m v ωv v , v v represents the radial velocity of the blade; F kp The Coriolis force of the pin satisfies the following formula: F kp =2m p ωv p , v prepresents the radial velocity of the pin; Fvv represents the friction force between the blade and the blade slot; Fvp represents the friction force between the pin and the pin slot; l1, l2 and lp1 represent the force arms of N1, N2 and Fp1 relative to the contact point between the blade and the inner surface of the annular stator respectively; tv represents the blade thickness; Lv represents the blade height.

[0094] S13: Substitute the equivalent curvature radius R and contact pressure W into the following formula established according to the elastohydrodynamic lubrication model:

[0095]

[0096] Among them, h min represents the minimum oil film thickness between the blade and the inner ring surface of the annular stator; α represents the oil viscosity-pressure coefficient; Represents the distance from the contact point between the blade tip and the annular stator to the center of the rotor; represents the angle of rotation of the rotating shaft 330; ω represents the rotor speed; R represents the equivalent radius of curvature; W represents the contact pressure; L represents the linear contact length between the blade tip and the inner surface of the annular stator;

[0097] E represents the equivalent elastic modulus between the blade and the annular stator, satisfying the following formula:

[0098]

[0099] Wherein, E1 and E2 represent the elastic modulus of blade and annular stator, respectively;

[0100] μ represents the current oil viscosity, which satisfies the following formula:

[0101]

[0102] Wherein, μ0 represents the viscosity of the oil at the initial temperature T0; P represents the load pressure, that is, the oil pressure in the oil pipe fed back by the pressure sensor; T represents the current oil temperature, that is, the oil temperature fed back by the thermometer;

[0103] S14: Get the calculation formula h of the minimum oil film thickness between the blade and the inner ring surface of the annular stator min =H(T,P,p d ,ω). Among them, H() represents the calculation function of the minimum oil film thickness, P represents the load pressure, p d Indicates the internal pressure of the cavity at the root of the pin groove.

[0104] like Figure 7The figure shows the comparison of the film thickness ratio before and after the optimization of the pin-type double-acting vane pump control method provided by the present application. It can be seen that under the initial working conditions of 800rpm, 20MPa load pressure and 46°C oil temperature, the film thickness ratio is lower than 1.5, and the blade tip and stator curved surface are seriously worn. According to the method provided by the present application, after adjusting the current of the electromagnetic inverse proportional pressure reducing valve and reducing the pressure of the pin bottom cavity, the film thickness ratio can be between 1.5 and 3, which can reduce friction and wear, and reduce oil leakage at the blade tip.

[0105] The expressions "first", "second", "the first" or "the second" used in various embodiments of the present disclosure may modify various components regardless of order and / or importance, but these expressions do not limit the corresponding components. The above expressions are only configured for the purpose of distinguishing an element from other elements. For example, a first user device and a second user device represent different user devices, although both are user devices. For example, a first element may be referred to as a second element, and similarly, a second element may be referred to as a first element without departing from the scope of the present disclosure.

[0106] When one element (e.g., a first element) is referred to as being "(operably or communicatively) coupled" or "(operably or communicatively) coupled to" or "connected to" another element (e.g., a second element), it is understood that the one element is directly connected to the other element or the one element is indirectly connected to the other element via yet another element (e.g., a third element). Conversely, it is understood that when an element (e.g., a first element) is referred to as being "directly connected" or "directly coupled" to another element (the second element), no element (e.g., a third element) is interposed between the two.

[0107] It should be noted that, in this article, the terms "include", "comprises" or any other variants thereof are intended to cover non-exclusive inclusion, so that a process, method, article or device including a series of elements includes not only those elements, but also includes other elements not explicitly listed, or also includes elements inherent to such process, method, article or device. In the absence of further restrictions, an element defined by the sentence "includes a ..." does not exclude the existence of other identical elements in the process, method, article or device including the element. In addition, components, features, and elements with the same name in different embodiments of the present application may have the same meaning or different meanings, and their specific meanings need to be determined by their explanation in the specific embodiment or further combined with the context of the specific embodiment.

[0108] The above description is only an optional embodiment of the present application and an explanation of the technical principles used. Those skilled in the art should understand that the scope of the invention involved in the present application is not limited to the technical solution formed by a specific combination of the above technical features, but should also cover other technical solutions formed by any combination of the above technical features or their equivalent features without departing from the above invention concept. For example, the above features are replaced with the technical features with similar functions disclosed in this application (but not limited to) by each other.

[0109] As used herein, the words "if" and "if" may be interpreted as "at the time of" or "when" or "in response to determining" or "in response to detecting", depending on the context. Similarly, the phrases "if it is determined" or "if (stated condition or event) is detected" may be interpreted as "when it is determined" or "in response to determining" or "when detecting (stated condition or event)" or "in response to detecting (stated condition or event)", depending on the context.

[0110] The above description is only an optional embodiment of the present application and an explanation of the technical principles used. Those skilled in the art should understand that the scope of the invention involved in the present application is not limited to the technical solution formed by a specific combination of the above technical features, but should also cover other technical solutions formed by any combination of the above technical features or their equivalent features without departing from the above invention concept. For example, the above features are replaced with the technical features with similar functions disclosed in this application (but not limited to) by each other.

[0111] The above description is only an optional embodiment of the present application and is not intended to limit the present application. For those skilled in the art, the present application may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1. A control method for a pin-type double-acting vane pump with improved lubrication characteristics, the method being applied to a controller of a pin-type double-acting vane pump control system, The pin-type double-acting vane pump structure with improved lubrication properties comprises: An electromagnetic inverse proportional pressure reducing valve and a front distribution plate, a rotating assembly and a rear distribution plate which are stacked in sequence; the rotating assembly comprises an annular stator, a rotor and a motor; the rotor rotates around the rotor center in the annular interior of the annular stator driven by the rotating shaft of the motor; the rotor is provided with an equal number of pin grooves and blade grooves which are interconnected, a pin is provided in the pin groove, a blade is provided in the blade groove, and the rotor cross section is centrally symmetrical about the center of the rotor; when the rotor rotates, the blade is pressed against the inner ring surface of the annular stator under the action of the high-pressure oil in the root cavity of the pin groove; the root cavity of the pin groove is connected to the high-pressure cavity of the rear distribution plate through the electromagnetic inverse proportional pressure reducing valve, and the electromagnetic inverse proportional pressure reducing valve is used to adjust the oil pressure of the root cavity; the rotor is provided with at least one guide hole which is connected to the root cavity of the pin groove; the rear distribution plate is provided with a guide hole which is connected to the guide hole The oil inlet of the electromagnetic inverse proportional pressure reducing valve is connected to the high-pressure chamber on the rear distribution plate, and the oil outlet of the electromagnetic inverse proportional pressure reducing valve is connected to the U-shaped groove on the rear distribution plate; the pin-type double-acting vane pump control system for improving lubrication characteristics includes: an oil tank, a pin-type double-acting vane pump structure, a controller, and a speed sensor, a thermometer, and a pressure sensor electrically connected to the controller; the controller is also electrically connected to the electromagnetic inverse proportional pressure reducing valve; the speed sensor is arranged on the rotating shaft of the motor to detect the rotation speed of the rotor; the oil suction port of the pin-type double-acting vane pump structure is connected to the oil tank, and the oil outlet of the pin-type double-acting vane pump structure is connected to the external load system through an oil pipe; the thermometer and the pressure sensor are arranged on the oil pipe, the thermometer is used to detect the oil temperature in the oil pipe, and the pressure sensor is used to detect the oil pressure in the oil pipe; Characterized in that the method comprises the following steps: S1: establishing a calculation formula for the minimum oil film thickness between the blade and the inner ring surface of the annular stator according to an elastohydrodynamic lubrication model; S2: Substituting the rotor speed fed back by the speed sensor and the oil temperature fed back by the thermometer into the calculation formula of the minimum oil film thickness, and substituting the oil pressure fed back by the pressure sensor as the load pressure into the calculation formula of the minimum oil film thickness, to obtain a relationship between the minimum oil film thickness and the pressure inside the cavity of the root of the pin groove; S3: Calculating, according to the relationship, a target pressure range of the cavity pressure when the minimum oil film thickness reaches a target thickness range; S4: controlling the electromagnetic inverse proportional pressure reducing valve to adjust the pressure in the cavity at the root of the pin groove to be within the target pressure range; The S1 includes: S11: Calculating the equivalent radius of curvature R between the top of the blade and the inner ring surface of the annular stator according to the analysis of the pin-type double-acting vane pump structure; S12: solving the contact pressure W between the blade tip and the inner ring surface of the annular stator according to the force balance equation; S13: Substitute the equivalent curvature radius R and the contact pressure W into the following formula established according to the elastohydrodynamic lubrication model: Among them, h min represents the minimum oil film thickness between the blade and the inner ring surface of the annular stator; α represents the oil viscosity-pressure coefficient; represents the distance from the contact point between the blade tip and the annular stator to the center of the rotor; represents the angle of rotation of the rotating shaft; ω represents the rotor speed; R represents the equivalent radius of curvature; W represents the contact pressure; L represents the linear contact length between the tip of the blade and the inner surface of the annular stator; E represents the equivalent elastic modulus between the blade and the annular stator, satisfying the following formula: Wherein, E1 and E2 represent the elastic modulus of blade and annular stator, respectively; μ represents the current oil viscosity, which satisfies the following formula: Wherein, μ0 represents the viscosity of the oil at the initial temperature T0; P represents the load pressure, that is, the oil pressure in the oil pipe fed back by the pressure sensor; T represents the current oil temperature, that is, the oil temperature fed back by the thermometer; S14: Obtain a calculation formula h for the minimum oil film thickness between the blade and the inner ring surface of the annular stator min =H(T,P,p d ,ω), where H() represents the calculation function of the minimum oil film thickness; p d Indicates the pressure inside the cavity at the root of the pin groove; The target thickness range is: Among them, R a1 represents the roughness of the blade tip, R a2 represents the roughness of the inner surface of the annular stator; The S12 includes: The contact pressure W between the blade tip and the inner ring surface of the annular stator is solved according to the following force balance equation: Wherein, f1 represents the friction coefficient between the blade and the rotor; f2 represents the friction coefficient between the blade and the annular stator; N1 and N2 represent the contact force between the blade and the two sides of the blade slot respectively; γ represents the angle between the contact pressure W between the blade tip and the inner ring surface of the annular stator and the blade radial direction; F p1 、F p2 and F p3 Respectively represent the oil pressure at the front side, rear side and top end of the blade; F dv Indicates the oil pressure at the bottom of the blade; F dp The oil pressure in the cavity at the root of the pin groove satisfies the following formula: F dp =πd 2 p d / 4; F cv represents the centrifugal force of the blade, satisfying the following formula: F cv =m v l cv ω 2 , where m v represents the mass of the blade, l cv represents the distance between the blade and the center of the rotor, ω represents the rotor speed; F cp The centrifugal force of the pin satisfies the following formula: F cp =m p l cp ω 2 , where m p represents the mass of the pin, l cp represents the distance between the pin and the center of the rotor; F av The inertial force generated by the radial acceleration of the blade satisfies the following formula: F av =m v a v , a v represents the radial acceleration of the blade; F ap The inertial force generated by the radial motion acceleration of the pin satisfies the following formula: F ap =m p a p , a p represents the radial acceleration of the pin; F kv represents the Coriolis force of the blade, satisfying the following formula: F kv =2m v ωv v , v v represents the radial velocity of the blade; F kp The Coriolis force of the pin satisfies the following formula: F kp =2m p ωv p , v p represents the radial velocity of the pin; F vv represents the friction force between the blade and the blade groove; F vp represents the friction force between the pin and the pin groove; l1, l2 and l p1 Represents N1, N2 and F respectively p1 The moment arm relative to the contact point between the blade and the inner surface of the annular stator; t v Indicates the thickness of the blade; L v Indicates the blade height.

2. The pin-type double-acting vane pump control method for improving lubrication characteristics according to claim 1, characterized in that: The S11 includes: The equivalent radius of curvature R between the blade tip and the inner ring surface of the annular stator is calculated according to the following formula: Wherein, r represents the fillet radius of the blade tip.

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