CN116305641A - Method and device for designing structural parameters of a pin-type double-acting vane pump - Google Patents

Abstract

The application discloses a structural parameter design method and device of a pin type double-acting vane pump. The structural parameter design method is a simulation method of flow pulsation and pressure pulsation of each cavity in the pin type double-acting vane pump under the current structural parameters, the flow/pressure characteristics of each cavity are simulated based on a liquid-solid coupling simulation model established by MATLAB Simulink simulation software, the influence of radial movement of the vane pins on each part of cavities inside is considered, and the simulation result has higher reliability. The structural parameter designer may seek the best design values for the individual structural parameters at a lower time cost by observing the flow and pressure profiles corresponding to the current structural parameter to adjust one or more of the current structural parameters.

Description

Method and device for designing structural parameters of a pin-type double-acting vane pump

technical field

The present application relates to the technical field of hydraulic transmission, in particular to a method and device for designing structural parameters of a pin-type double-acting vane pump.

Background technique

Pin-type double-acting vane pumps are widely used in construction machinery due to their advantages of high energy density and low noise. The inner surface, with the change of the stator curve, reciprocates in the vane groove. When the vane moves from the small diameter to the large diameter, the volume between the two vanes gradually increases, forming a partial vacuum and absorbing oil. When the vane moves from the large diameter When moving toward the small diameter, the volume between the two blades gradually decreases and the oil is discharged. The rotor rotates once, and the blades reciprocate twice in the groove, forming two oil suction and discharge.

Due to the influence of its internal structure, the pin-type double-acting vane pump has problems of leakage and flow pulsation, so it is necessary to optimize the design of its structural parameters. At present, in the design process of the structural parameters of the pin-type double-acting vane pump, it is necessary to establish a simulation model corresponding to the current structural parameters with the help of simulation technology, so as to simulate the flow/pressure characteristics of each cavity under the design of the current structural parameters, so as to assist the design. Personnel adjustments optimize current structural parameters.

However, the current simulation technology is difficult to consider the impact of each cavity in the pin-type double-acting vane pump, and the impact of the radial movement of the vane on the corresponding cavity, which makes the designed structural parameters far from the optimal parameters.

Contents of the invention

The purpose of the present application is to provide a structural parameter design method and device for a pin-type double-acting vane pump, which can improve the above-mentioned problems.

The embodiment of the application is realized like this:

The application provides a structural parameter design method of a pin-type double-acting vane pump, which includes:

S1. Obtain the current structural parameters of the pin-type double-acting vane pump;

S2, according to described current structure parameter, construct the liquid-solid coupling simulation model of described pin type double-acting vane pump in MATLAB Simulink simulation software;

S3. Obtain the initial pressure value and initial volume value of each cavity of the pin type double-acting vane pump;

S4. Bring the initial pressure value and the initial volume value into the liquid-solid coupling simulation model, and calculate according to the preset vane speed simulation that each cavity of the pin-type double-acting vane pump is within a single working cycle The flow characteristic curve and pressure characteristic curve.

Among them, S1, S2, etc. are only step identifiers, and the execution order of the method does not necessarily follow the order of numbers from small to large. For example, step S2 may be executed first, and then step S1 may be executed, which is not limited in this application.

It can be understood that this application discloses a structural parameter design method of a pin-type double-acting vane pump, which is actually a simulation method for the flow pulsation and pressure fluctuation of each cavity in the pin-type double-acting vane pump under the current structural parameters , based on the liquid-solid coupling simulation model established by MATLAB Simulink simulation software to simulate the flow/pressure characteristics of each cavity, considering the influence of the radial movement of the blade pin on the internal cavity of each part, the simulation results have a high degree of credibility . Structural parameter designers can adjust one or more of the current structural parameters by observing the flow characteristic curve and pressure characteristic curve corresponding to the current structural parameters, so as to seek the optimal design value of each structural parameter at a lower time cost.

In an optional embodiment of the present application, the current structural parameters include at least one of the following: blade number, blade length, blade tip height, blade thickness, pin diameter, and stator curve.

It can be understood that, based on the above simulation method, the influence of structural parameters such as the number of vanes, pin diameter, vane thickness, and stator curve type on the output flow pulsation and pressure pulsation of the pinned double-acting vane pump can be further studied. Cost seeks the optimum design value for each structural parameter.

In an optional embodiment of the present application, step S4 includes:

S41. The liquid-solid coupling simulation model simulates and calculates the flow characteristic curves of each cavity of the pin type double-acting vane pump in a single working cycle according to the preset vane speed;

S42. According to the initial pressure value of each chamber of the pin-type double-acting vane pump and the flow channel size between adjacent chambers, simulate and calculate the interactive flow rate of each chamber;

S43. According to the initial pressure value, the initial volume value, the interactive flow rate and the flow characteristic curve, simulate and calculate the pressure characteristics of each cavity of the pin-type double-acting vane pump in a single working cycle curve.

It can be understood that during the working process of the pin-type double-acting vane pump, the vanes and pins will move radially in the vane slots and pin slots respectively due to the restriction of the inner curve of the stator while following the rotating motion of the rotor. The radial movement of the blade and the pin will affect the volume change of the adjacent working chamber, the cavity at the bottom of the blade and the cavity at the bottom of the pin. Therefore, the liquid-solid coupling simulation model constructed according to the current structural parameters needs to simulate and calculate the pressure characteristic curve and flow characteristic curve of each cavity in a single working cycle, so as to fully consider the impact of each structural parameter on each capacity of the pin double-acting vane pump. The impact of the cavity makes the final designed structural parameters closer to the optimal parameters.

In an optional embodiment of the present application, the preset vane speed can be a default value, which is preset by the background; in addition, the preset vane speed can also be a custom value, which is determined by the design of the structural parameters of the pin type double-acting vane pump Personnel setting, before step S4, the structural parameter design method of the pin type double-acting vane pump also includes: obtaining the preset vane speed.

In an optional embodiment of the present application, step S41 includes:

The liquid-solid coupling simulation model simulates and calculates the flow characteristic curve _Qwc (t) of the working chamber of the pin type double-acting vane pump in a single working cycle according to the following formula:

With the tip of the blade in contact with the stator,

With the rear end of the blade in contact with the stator,

Among them, Q _wc (θ) represents the current volume flow rate of the working chamber, B represents the length of the blade, ω ₀ represents the preset blade speed, h _v represents the height of the blade tip, t _v represents the thickness of the blade, and v _v represents the radial direction of the blade Moving speed, N represents the number of blades, θ represents the position angle of the blade centerline.

In an optional embodiment of the present application, step S41 also includes:

The liquid-solid coupling simulation model simulates and calculates the flow characteristic curve Q _uv (t) of the vane bottom cavity of the pin type double-acting vane pump in a single working cycle according to the following formula:

Among them, Q _uv (θ) represents the current volume flow rate of the cavity at the bottom of the blade, B represents the length of the blade, ω ₀ represents the preset speed of the blade, t _p represents the diameter of the pin, t _v represents the thickness of the blade, and v _v represents the diameter of the blade to the speed of movement;

The liquid-solid coupling simulation model simulates and calculates the flow characteristic curve Q _up (t) of the pin bottom cavity of the pin double-acting vane pump in a single working cycle according to the following formula:

Among them, Q _up (θ) represents the current volume flow rate of the bottom cavity of the pin, N represents the number of blades, v _v represents the radial moving speed of the blades, ω ₀ represents the preset blade speed, t _p represents the diameter of the pin, k Represents a positive integer.

In an optional embodiment of the present application, step S42 includes:

S421. Calculate the initial pressure difference between adjacent chambers according to the initial pressure value of each chamber of the pin-type double-acting vane pump;

S422. Calculate the interaction flow of each cavity according to the initial pressure difference and the corresponding flow channel size.

In an optional embodiment of the present application, step S43 includes:

The liquid-solid coupling simulation model simulates and calculates the pressure characteristic curve p(t) of each cavity of the pin type double-acting vane pump in a single working cycle according to the following formula:

Wherein, p ₀ represents the initial pressure value, V ₀ represents the initial volume value, Q _ex (t) represents the exchange flow between the current chamber and other chambers, and Q _v (t) represents the flow rate of the current chamber characteristic curve.

In an optional embodiment of the present application, the method further includes:

S5. Determine the current pressure of the working chamber according to the pressure characteristic curve of the working chamber;

S6. Perform force analysis on the blade according to the current pressure to obtain the oil film supporting force between the blade and the stator;

S7. Calculate the thickness of the oil film at the tip of the blade according to the oil film support force and the current structural parameters;

S8. Comparing the oil film thickness with the inner surface roughness of the vane and the stator, and calculating a film thickness ratio parameter.

It can be understood that there is contact friction between the vane tip of the pin-type double-acting vane pump and the stator, which is prone to wear. The friction state between the blade and the rotor can be analyzed by calculating the film thickness ratio at the top of the blade, and then the influence of the operating parameters and structural parameters of the pin-type double-acting vane pump on its friction state can be analyzed. Provide a basis for performance optimization.

In an optional embodiment of the present application, step S7 includes:

S71. Calculate the viscous parameter and elastic parameter from the oil film supporting force and the current structural parameter according to the following formula:

表示所述叶子和所述定子表面间的当量曲率半径，其中，R₁表示所述定子的曲率半径，R₂表示所述叶片的曲率半径，L表示所述叶片与所述定子的表面的线接触长度，α表示油液的黏压系数，E表示所述叶子和所述定子表面间的当量弹性模量；Wherein, g _e represents the elastic parameter, g _v represents the viscosity parameter, η ₀ is the viscosity of the oil under normal pressure, W represents the dynamic pressure supporting force on the blade produced by the oil between the blade and the stator, where The size can be obtained through force analysis of the blade, U represents the entrainment velocity between the blade and the surface of the stator, which is approximately 0.5 times the rotational speed of the input shaft;

Represents the equivalent radius of curvature between the blade and the surface of the stator, wherein _R1 represents the radius of curvature of the stator, _R2 represents the radius of curvature of the blade, and L represents the line between the blade and the surface of the stator Contact length, α represents the viscosity-pressure coefficient of the oil, and E represents the equivalent modulus of elasticity between the leaf and the surface of the stator;

S72. Using the viscosity parameter and the elastic parameter as coordinate parameters, determine the target state area where the coordinate parameters are currently located in the Hooke lubrication state diagram;

S73. Calculate the oil film thickness at the tip of the blade according to the target state area.

In an optional embodiment of the present application, step S73 includes:

According to the following formula, the oil film thickness at the tip of the blade is calculated from the target state area:

表示所述目标状态区域为R-I区域时所述叶片顶端的油膜厚度，/>

表示所述目标状态区域为R-V区域时所述叶片顶端的油膜厚度，/>

表示所述目标状态区域为E-I区域时所述叶片顶端的油膜厚度，/>

表示所述目标状态区域为E-V区域时所述叶片顶端的油膜厚度。其中，in,

Indicates the oil film thickness at the top of the blade when the target state area is the RI area, />

Indicates the oil film thickness at the top of the blade when the target state area is the RV area, />

Indicates the oil film thickness at the tip of the blade when the target state area is the EI area, />

Indicates the oil film thickness at the tip of the blade when the target state area is the EV area. in,

In an optional embodiment of the present application, step S8 includes:

Calculate the film thickness ratio parameter according to the following formula:

Wherein, λ represents the film thickness ratio parameter, h _min represents the thickness of the oil film at the top of the blade, R _α1 represents the roughness of the inner surface of the blade, and R _α2 represents the roughness of the inner surface of the stator.

It can be understood that the friction state between the blade and the stator can be judged according to the film thickness ratio parameter λ. When λ<1, the friction state between the blade and the stator surface is boundary friction; when 1<λ<3, the blade and the stator surface are in a mixed friction state; when λ>3, the blade and the stator surface are fluid friction state. In general, when λ>1.5, the friction pair can work normally.

Beneficial effect:

This application discloses a structural parameter design method of a pin-type double-acting vane pump, which is actually a simulation method for the flow pulsation and pressure fluctuation of each cavity in the pin-type double-acting vane pump under the current structural parameters. The designer can adjust one or more of the current structural parameters by observing the flow characteristic curve and pressure characteristic curve corresponding to the current structural parameters, so as to seek the optimal design value of each structural parameter at a lower time cost.

During the working process of the pin-type double-acting vane pump, the vane and the pin follow the rotor to rotate and move radially in the vane groove and the pin groove respectively due to the restriction of the inner curve of the stator. The radial movement of the blade and the pin will affect the volume change of the adjacent working chamber, the cavity at the bottom of the blade and the cavity at the bottom of the pin. Therefore, based on the MATLAB Simulink simulation software, the liquid-solid coupling simulation model constructed according to the current structural parameters needs to simulate and calculate the pressure characteristic curve and flow characteristic curve of each cavity in a single working cycle, so as to fully consider the impact of each structural parameter on the pin type double Due to the influence of each cavity in the vane pump, the simulation results have a high degree of reliability, making the final designed structural parameters closer to the optimal parameters.

In addition, there is contact friction between the tip of the vane of the pin-type double-acting vane pump and the stator, which is prone to wear. The friction state between the blade and the rotor can be analyzed by calculating the film thickness ratio at the top of the blade, and then the influence of the operating parameters and structural parameters of the pin-type double-acting vane pump on its friction state can be analyzed. Provide a basis for performance optimization.

In order to make the above-mentioned purpose, features and advantages of the present application more comprehensible, optional embodiments are specifically cited below, together with the accompanying drawings, and described in detail as follows.

Description of drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present application, the accompanying drawings that are required in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of the present application, and thus It should be regarded as a limitation on the scope, and those skilled in the art can also obtain other related drawings based on these drawings without creative work.

Fig. 1 is a cross-sectional view of a rotor and a stator of a pin type double-acting vane pump provided by the present application;

Fig. 2 is a cross-sectional view of a valve plate of a pin type double-acting vane pump provided by the present application;

Fig. 3 is an enlarged schematic view of the blade portion shown in Fig. 1;

Fig. 4 is a schematic flow chart of a structural parameter design method of a pin-type double-acting vane pump provided by the present application;

Fig. 5 is the Hooke lubrication state figure that the application provides;

Fig. 6 is the simulation result figure that the blade top oil film thickness changes with the rotation angle that the application provides;

Fig. 7 is a simulation result diagram of the variation of the film thickness ratio with the rotation angle provided by the present application.

Figure number:

Stator 1, rotor 2, blade 3, pin 4, low-pressure working chamber 61 and 62, blade bottom chamber 7, pin bottom chamber 8, high-pressure working chamber 91 and 92, rotor cross-section oil hole 10, oil-absorbing area waist Type groove 11, pressure equalizing groove 12 in oil suction area, distribution plate 13, pressure equalizing groove 14 in oil discharge area, oil passage groove 15, waist groove 16 in oil discharge area, oil discharge areas 31 and 32, oil suction areas 33 and 34.

Detailed ways

The following will clearly and completely describe the technical solutions in the embodiments of the application with reference to the drawings in the embodiments of the application. Apparently, the described embodiments are only some of the embodiments of the application, not all of them. Based on the embodiments in this application, all other embodiments obtained by persons of ordinary skill in the art without creative efforts fall within the protection scope of this application.

As shown in Figure 1, it is a sectional view of the rotor and the stator of the double-acting vane pump with pins. In the figure, there are two low-pressure working chambers (61, 62) and two high-pressure working chambers (91) between the stator 1 and the rotor 2. ,92). The rotor 2 can rotate around the input shaft 5, and the periphery of the stator 1 is radially provided with a plurality of interconnected blade slots and pin slots, as shown in Figure 3, the blade 3 can perform radial movement in the blade slot, and the pin 4 Radial movement can be made in the pin groove, a blade bottom cavity 7 is set between the blade groove and the pin groove, and the pin bottom cavity 8 is connected to the end of the pin groove away from the blade bottom cavity 7 . Between the rotor 2 and the input shaft 5 are also provided a plurality of rotor section oil through holes 10 .

As shown in Figure 2, it is a cross-sectional view of the distribution plate of the pin type double-acting vane pump. The central position of the distribution plate 13 is provided with a through hole for accommodating the input shaft 5, and the distribution plate 13 is provided with two symmetrically arranged with respect to the through hole. There are two oil discharge areas (31,32) and two oil absorption areas (33 and 34). The oil discharge area is equipped with the oil discharge area pressure equalization groove 14 and the oil discharge area waist groove 16 connected by the oil passage groove 15, and the oil suction area is equipped with the independent oil absorption area waist groove 11 and the oil absorption area pressure equalization groove 12. A circular arc area is arranged between the adjacent oil discharge area and the oil suction area, and the radians of the adjacent arc areas are different. As shown in Figure 2, the arc area between the oil discharge area 31 and the oil suction area 33 and the arc area between the oil discharge area 32 and the oil absorption area 34 are small arc areas, and the area between the oil discharge area 31 and the oil absorption area 34 The arc area between the oil discharge area 32 and the oil suction area 33 is a large arc area, and the arc degree of the large arc area is greater than that of the small arc area.

In the pin-type double-acting vane pump, the rotor 2 and the distribution plate 13 are stacked. When working, the rotor 2 rotates around the input shaft 5, and the vane 3 will be thrown out with the centrifugal force and the high-pressure oil at the bottom of the vane 3, and it will be close to the inside of the stator 1. On the surface, with the change of the curve of the stator 1, it reciprocates in the vane groove. When the vane 3 moves from the small diameter to the large diameter, the volume between the two vanes 3 gradually increases, forming a partial vacuum and absorbing oil. When the vane 3 When moving from the large diameter to the small diameter, the volume between the two blades 3 gradually decreases to discharge oil, the rotor 2 rotates once, and the blades 3 reciprocate twice in the groove, forming two oil suction and discharge.

Due to the influence of its internal structure, the pin-type double-acting vane pump has problems of leakage and flow pulsation, so it is necessary to optimize the design of its structural parameters. At present, in the design process of the structural parameters of the pin-type double-acting vane pump, it is necessary to establish a simulation model corresponding to the current structural parameters with the help of simulation technology, so as to simulate the flow/pressure characteristics of each cavity under the design of the current structural parameters, so as to assist the design. Personnel adjustments optimize current structural parameters.

However, the current simulation technology is difficult to consider the impact of each cavity in the pin-type double-acting vane pump, and the impact of the radial movement of the vane on the corresponding cavity, which makes the designed structural parameters far from the optimal parameters.

In order to solve the above problems, in the first aspect, as shown in Figure 4, the present application provides a structural parameter design method of a pin-type double-acting vane pump, which includes:

S1. Obtain the current structural parameters of the pin-type double-acting vane pump.

In an optional embodiment of the present application, the current structural parameters include at least one of the following: blade number, blade length, blade tip height, blade thickness, pin diameter, and stator curve.

S2. According to the current structural parameters, construct a liquid-solid coupling simulation model of a pin-type double-acting vane pump in the simulation software MATLAB Simulink.

S3. Obtain the initial pressure value and initial volume value of each chamber of the pin-type double-acting vane pump.

S4. Bring the initial pressure value and initial volume value into the liquid-solid coupling simulation model, and calculate the flow characteristic curve and pressure characteristic curve of each cavity of the pin type double-acting vane pump in a single working cycle according to the preset vane speed simulation .

Among them, S1, S2, etc. are only step identifiers, and the execution order of the method does not necessarily follow the order of numbers from small to large. For example, step S2 may be executed first, and then step S1 may be executed, which is not limited in this application.

It can be understood that this application discloses a structural parameter design method of a pin-type double-acting vane pump, which is actually a simulation method for the flow pulsation and pressure fluctuation of each cavity in the pin-type double-acting vane pump under the current structural parameters , based on the liquid-solid coupling simulation model established by MATLAB Simulink simulation software to simulate the flow/pressure characteristics of each cavity, considering the influence of the radial movement of the blade pin on the internal cavity of each part, the simulation results have a high degree of credibility . Structural parameter designers can adjust one or more of the current structural parameters by observing the flow characteristic curve and pressure characteristic curve corresponding to the current structural parameters, so as to seek the optimal design value of each structural parameter at a lower time cost.

It can be understood that, based on the above simulation method, the influence of structural parameters such as the number of vanes, pin diameter, vane thickness, and stator curve type on the output flow pulsation and pressure pulsation of the pinned double-acting vane pump can be further studied. Cost seeks the optimum design value for each structural parameter.

In an optional embodiment of the present application, step S4 includes:

S41. The liquid-solid coupling simulation model simulates and calculates flow characteristic curves of each cavity of the pin-type double-acting vane pump in a single working cycle according to the preset vane speed.

In an optional embodiment of the present application, the preset vane speed can be a default value, which is preset by the background; in addition, the preset vane speed can also be a custom value, which is determined by the design of the structural parameters of the pin type double-acting vane pump Personnel setting, before step S4, the structural parameter design method of the pin type double-acting vane pump also includes: obtaining the preset vane speed.

S42. According to the initial pressure value of each chamber of the pin-type double-acting vane pump and the size of the flow channel between adjacent chambers, simulate and calculate the interaction flow of each chamber.

S43. According to the initial pressure value, the initial volume value, the interactive flow rate and the flow characteristic curve, simulate and calculate the pressure characteristic curve of each cavity of the pin-type double-acting vane pump in a single working cycle.

It can be understood that during the working process of the pin-type double-acting vane pump, the vanes and pins will move radially in the vane slots and pin slots respectively due to the restriction of the inner curve of the stator while following the rotating motion of the rotor. The radial movement of the blade and the pin will affect the volume change of the adjacent working chamber, the cavity at the bottom of the blade and the cavity at the bottom of the pin. Therefore, the liquid-solid coupling simulation model constructed according to the current structural parameters needs to simulate and calculate the pressure characteristic curve and flow characteristic curve of each cavity in a single working cycle, so as to fully consider the impact of each structural parameter on each capacity of the pin double-acting vane pump. The impact of the cavity makes the final designed structural parameters closer to the optimal parameters.

In an optional embodiment of the present application, step S41 includes:

The liquid-solid coupling simulation model simulates and calculates the flow characteristic curve Q _wc (t) of the working chamber of the pin-type double-acting vane pump in a single working cycle according to the following formula:

With the tip of the blade in contact with the stator,

With the rear end of the blade in contact with the stator,

Among them, Q _wc (θ) represents the current volume flow of the working chamber, B represents the length of the blade, ω ₀ represents the preset blade speed, h _v represents the height of the blade tip, t _v represents the thickness of the blade, and v _v represents the radial moving speed of the blade , N represents the number of blades, θ represents the position angle of the blade centerline.

In an optional embodiment of the present application, step S41 also includes:

The liquid-solid coupling simulation model simulates and calculates the flow characteristic curve Q _uv (t) of the cavity at the bottom of the vane of the pin double-acting vane pump in a single working cycle according to the following formula:

Among them, Q _uv (θ) represents the current volume flow of the cavity at the bottom of the blade, B represents the length of the blade, ω ₀ represents the preset blade speed, t _p represents the diameter of the pin, t _v represents the thickness of the blade, and v _v represents the radial movement of the blade speed;

The liquid-solid coupling simulation model simulates and calculates the flow characteristic curve Q _up (t) of the pin bottom cavity of the pin double-acting vane pump in a single working cycle according to the following formula:

Among them, Q _up (θ) represents the current volumetric flow rate of the bottom cavity of the pin, N represents the number of blades, v _v represents the radial moving speed of the blades, ω ₀ represents the preset blade speed, t _p represents the diameter of the pin, k represents positive integer.

In an optional embodiment of the present application, step S42 includes:

S421. Calculate the initial pressure difference between adjacent chambers according to the initial pressure value of each chamber of the pin-type double-acting vane pump;

S422. Calculate the interactive flow rate of each cavity according to the initial pressure difference and the corresponding flow channel size.

In an optional embodiment of the present application, step S43 includes:

The liquid-solid coupling simulation model simulates and calculates the pressure characteristic curve p(t) of each cavity of the pin type double-acting vane pump in a single working cycle according to the following formula:

Among them, p ₀ represents the initial pressure value, V ₀ represents the initial volume value, Q _ex (t) represents the exchange flow between the current chamber and other chambers, and Q _v (t) represents the flow characteristic curve of the current chamber.

In an optional embodiment of the present application, the method further includes:

S5. Determine the current pressure of the working chamber according to the pressure characteristic curve of the working chamber.

S6. Perform force analysis on the blade according to the current pressure to obtain the oil film supporting force between the blade and the stator.

S7. Calculate the thickness of the oil film at the tip of the blade according to the oil film supporting force and the current structural parameters.

S8. Comparing the oil film thickness with the inner surface roughness of the vane and the stator, and calculating a film thickness ratio parameter.

It can be understood that there is contact friction between the vane tip of the pin-type double-acting vane pump and the stator, which is prone to wear. The friction state between the blade and the rotor can be analyzed by calculating the film thickness ratio at the top of the blade, and then the influence of the operating parameters and structural parameters of the pin-type double-acting vane pump on its friction state can be analyzed. Provide a basis for performance optimization.

The change of the pressure characteristic curve in at least one working cycle can calculate the change of the oil film thickness at the top of the blade with the rotation angle, and the change of the film thickness ratio with the rotation angle can also be calculated. Figure 6 shows the simulation results of the change of the oil film thickness at the top of the blade with the rotation angle Figure 7 shows the simulation results of the film thickness ratio changing with the rotation angle. Obtaining the simulation results in Figure 6 and Figure 7 is helpful for designers to analyze the impact of the operating parameters and structural parameters of the pin-type double-acting vane pump on its friction state, so as to find more suitable structural parameters.

In an optional embodiment of the present application, step S7 includes:

S71. Calculate the viscous parameter and elastic parameter from the oil film supporting force and the current structural parameter according to the following formula:

表示所述叶子和所述定子表面间的当量曲率半径，其中，R₁表示所述定子的曲率半径，R₂表示所述叶片的曲率半径，L表示所述叶片与所述定子的表面的线接触长度，α表示油液的黏压系数，E表示所述叶子和所述定子表面间的当量弹性模量；其中，其中g_e和g_v分别表征固体弹性和油液黏性对油膜厚度的影响大小。Wherein, g _e represents the elastic parameter, g _v represents the viscosity parameter, η ₀ is the viscosity of the oil under normal pressure, W represents the dynamic pressure supporting force on the blade produced by the oil between the blade and the stator, where The size can be obtained through force analysis of the blade, U represents the entrainment velocity between the blade and the surface of the stator, which is approximately 0.5 times the rotational speed of the input shaft;

Represents the equivalent radius of curvature between the blade and the surface of the stator, wherein _R1 represents the radius of curvature of the stator, _R2 represents the radius of curvature of the blade, and L represents the line between the blade and the surface of the stator Contact length, α represents the viscosity-pressure coefficient of the oil, and E represents the equivalent elastic modulus between the leaf and the surface of the stator; where g _e and g _v respectively represent the influence of solid elasticity and oil viscosity on the thickness of the oil film Impact size.

S72. Using the viscosity parameter and the elasticity parameter as coordinate parameters, determine the target state area where the coordinate parameters are currently located in the Hooke lubrication state diagram.

Figure 5 shows the Hooke lubrication state diagram. It can be seen that the abscissa is the elastic parameter g _e , and the ordinate is the viscous parameter g _v . The current state in the Hooke lubrication state diagram can be determined according to the coordinate parameters (ge _e , g _v ). The target state area is the RI area, the RV area, the EI area or the EV area.

S73. Calculate the oil film thickness at the tip of the blade according to the target state area.

In an optional embodiment of the present application, step S73 includes:

According to the following formula, the oil film thickness at the tip of the blade is calculated from the target state area:

表示所述目标状态区域为R-I区域时所述叶片顶端的油膜厚度，/>

表示所述目标状态区域为R-V区域时所述叶片顶端的油膜厚度，/>

表示所述目标状态区域为E-I区域时所述叶片顶端的油膜厚度，/>

表示所述目标状态区域为E-V区域时所述叶片顶端的油膜厚度。其中，in,

Indicates the oil film thickness at the top of the blade when the target state area is the RI area, />

Indicates the oil film thickness at the top of the blade when the target state area is the RV area, />

Indicates the oil film thickness at the tip of the blade when the target state area is the EI area, />

Indicates the oil film thickness at the tip of the blade when the target state area is the EV area. in,

In an optional embodiment of the present application, step S8 includes:

Calculate the film thickness ratio parameter according to the following formula:

Wherein, λ represents the film thickness ratio parameter, h _min represents the thickness of the oil film at the top of the blade, R _α1 represents the roughness of the inner surface of the blade, and R _α2 represents the roughness of the inner surface of the stator.

It can be understood that the friction state between the blade and the stator can be judged according to the film thickness ratio parameter λ. When λ<1, the friction state between the blade and the stator surface is boundary friction; when 1<λ<3, the blade and the stator surface are in a mixed friction state; when λ>3, the blade and the stator surface are fluid friction state. In general, when λ>1.5, the friction pair can work normally.

In a second aspect, the present application provides a device for designing structural parameters of a pin-type double-acting vane pump. The structural parameter design device of the pin type double-acting vane pump includes one or more processors and memory. The aforementioned processor and memory are connected via a bus. The memory is used to store a computer program including program instructions, and the processor is used to execute the program instructions stored in the memory. Wherein, the processor is configured to invoke the program instructions to execute the operations of any one of the methods in the first aspect.

It should be understood that in the embodiment of the present invention, the so-called processor may be a central processing unit (Central Processing Unit, CPU), and the processor may also be other general-purpose processors, digital signal processors (Digital Signal Processor, DSP), dedicated integrated Circuit (Application Specific Integrated Circuit, ASIC), off-the-shelf programmable gate array (Field-Programmable Gate Array, 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 be any conventional processor, or the like.

The memory, which can include read only memory and random access memory, provides instructions and data to the processor. A portion of the memory may also include non-volatile random access memory. For example, the memory may also store device type information.

The expression "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 configured only for the purpose of distinguishing an element from other elements. For example, the first user equipment and the second user equipment represent different user equipments, although both are user equipments. For example, a first element could be termed a second element, and, similarly, a second element could be termed a first element, without departing from the scope of the present disclosure.

When an element (eg, a first element) is referred to as being "(operably or communicably) coupled" or "(operably or communicably) coupled to" another element (eg, a second element) When an element (eg, a second element) is or is "connected to" another element (eg, a second element), it should be understood that the one element is directly connected to the other element or that the one element is connected via another element (eg, a second element). third element) is indirectly connected to the other element. In contrast, it will be understood that when an element (eg, a first element) is referred to as being "directly connected" or "directly coupled" to another element (eg, a second element), no element (eg, a third element) is interposed between the two. between.

It should be noted that, in this document, the term "comprising", "comprising" or any other variation thereof is intended to cover a non-exclusive inclusion such that a process, method, article or apparatus comprising a set of elements includes not only those elements, It also includes other elements not expressly listed, or elements inherent in the process, method, article, or device. Without further limitations, an element defined by the statement "comprising a..." does not exclude the presence of other identical elements in the process, method, article, or device that includes the element. In addition, different implementations of the present application Components, features, and elements with the same name in the example may have the same meaning, or may have different meanings, and the specific meaning shall be determined based on the explanation in the specific embodiment or further combined with the context in the specific embodiment.

The above description is only an optional embodiment of the present application and an illustration of the applied technical principle. Those skilled in the art should understand that the scope of the invention involved in this application is not limited to the technical solution formed by the specific combination of the above-mentioned technical features, and should also cover the technical solution formed by the above-mentioned technical features or Other technical solutions formed by any combination of equivalent features. For example, a technical solution formed by replacing the above-mentioned features with technical features with similar functions disclosed in (but not limited to) this application.

Depending on the context, the words "if", "if" as used herein may be interpreted as "at" or "when" or "in response to determining" or "in response to detecting". Similarly, depending on the context, the phrases "if determined" or "if detected (the stated condition or event)" could be interpreted as "when determined" or "in response to the determination" or "when detected (the stated condition or event) )" or "in response to detection of (a stated condition or event)".

The above description is only an optional embodiment of the present application and an illustration of the applied technical principle. Those skilled in the art should understand that the scope of the invention involved in this application is not limited to the technical solution formed by the specific combination of the above-mentioned technical features, and should also cover the technical solution formed by the above-mentioned technical features or Other technical solutions formed by any combination of equivalent features. For example, a technical solution formed by replacing the above-mentioned features with technical features with similar functions disclosed in (but not limited to) this application.

The above descriptions are only optional embodiments of the present application, and are not intended to limit the present application. For those skilled in the art, various modifications and changes may be made to the present application. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principles of this application shall be included within the protection scope of this application.

Claims (10)

1. The structural parameter design method of the pin type double-acting vane pump is characterized by comprising the following steps of:

acquiring the current structural parameters of the pin type double-acting vane pump;

according to the current structural parameters, constructing a liquid-solid coupling simulation model of the pin type double-acting vane pump in MATLAB Simul ink simulation software;

acquiring an initial pressure value and an initial volume value of each cavity of the pin type double-acting vane pump;

and carrying the initial pressure value and the initial volume value into the liquid-solid coupling simulation model, and calculating a flow characteristic curve and a pressure characteristic curve of each cavity of the pin type double-acting vane pump in a single working period according to the simulation of the preset vane rotating speed.

2. The method for designing structural parameters of a dual acting vane pump of claim 1, wherein,

the step of bringing the initial pressure value and the initial volume value into the liquid-solid coupling simulation model, and calculating flow characteristic curves and pressure characteristic curves of all the cavities of the pin type double-acting vane pump in a single working period according to preset vane rotating speed simulation, wherein the step of:

the liquid-solid coupling simulation model calculates flow characteristic curves of all the cavities of the pin type double-acting vane pump in a single working period according to the simulation of the preset vane rotating speed;

according to the initial pressure value of each cavity of the pin type double-acting vane pump and the size of a flow channel between adjacent cavities, the interactive flow of each cavity is calculated in a simulation mode;

and according to the initial pressure value, the initial volume value, the interactive flow and the flow characteristic curve, simulating and calculating the pressure characteristic curve of each cavity of the pin type double-acting vane pump in a single working period.

3. The method for designing structural parameters of a dual acting vane pump of claim 2, wherein,

the liquid-solid coupling simulation model calculates flow characteristic curves of all the cavities of the pin type double-acting vane pump in a single working period according to the simulation of the preset vane rotating speed, and the flow characteristic curves comprise:

the liquid-solid coupling simulation model calculates the flow characteristic curve Q of the working cavity of the pin type double-acting vane pump in a single working period in a simulation manner according to the following formula _wc (t)：

In the case where the front ends of the blades are in contact with the stator,

in the case where the rear ends of the blades are in contact with the stator,

wherein Q is _wc (θ) represents the current volumetric flow of the working volume, B represents the vane length, ω ₀ Representing the preset blade rotation speed, h _v Representing blade tip height, t _v Representing blade thickness, v _v Represents the radial moving speed of the blade, N represents the number of the blades, and theta represents the position angle of the center line of the blade.

4. The method for designing structural parameters of a dual acting vane pump of claim 3, wherein,

the liquid-solid coupling simulation model calculates flow characteristic curves of all the cavities of the pin type double-acting vane pump in a single working period according to the simulation of the preset vane rotating speed, and the flow characteristic curves further comprise:

the liquid-solid coupling simulation model calculates the flow characteristic curve Q of the bottom blade cavity of the pin type double-acting vane pump in a single working period according to the following simulation _uv (t)：

Wherein Q is _uv (θ) represents the current volumetric flow of the blade bottom pocket, B represents the blade length, ω ₀ Representing the preset blade rotation speed, t _p Represents the diameter of the pin, t _v Representing blade thickness, v _v Representing the radial movement speed of the blade;

the liquid-solid coupling simulation model calculates the flow characteristic curve Q of the pin bottom cavity of the pin type double-acting vane pump in a single working period according to the following simulation _up (t)：

Wherein Q is _up (θ) represents the current volumetric flow of the bottom cavity of the pin, N represents the number of blades, v _v Representing the speed of radial movement of the blade, ω ₀ Representing the preset blade rotation speed, t _p Represents the pin diameter, and k represents a positive integer.

5. The method for designing structural parameters of a dual acting vane pump of claim 2, wherein,

according to the initial pressure value of each cavity of the pin type double-acting vane pump and the size of a flow channel between adjacent cavities, the interactive flow of each cavity is calculated, and the method comprises the following steps:

calculating initial pressure differences between adjacent cavities according to initial pressure values of all cavities of the pin type double-acting vane pump;

and calculating the interactive flow of each cavity according to the initial pressure difference and the corresponding runner size.

6. The method for designing structural parameters of a dual acting vane pump of claim 2, wherein,

and according to the initial pressure value, the initial volume value, the interactive flow and the flow characteristic curve, calculating the pressure characteristic curve of each cavity of the pin type double-acting vane pump in a single working period in a simulation way, wherein the method comprises the following steps:

the liquid-solid coupling simulation model simulates and calculates the pressure characteristic curve p (t) of each cavity of the pin type double-acting vane pump in a single working period according to the following steps:

wherein p is ₀ Representing the initial pressure value, V ₀ Representing the initial volume value, Q _ex (t) represents the exchange flow rate between the current cavity and other cavities, Q _v And (t) represents the flow characteristic curve of the current cavity.

7. The structural parameter design method of a dual acting vane pump of claim 1 further comprising:

determining the current pressure of the working cavity according to the pressure characteristic curve of the working cavity;

carrying out stress analysis on the blade according to the current pressure to obtain an oil film supporting force between the blade and the stator;

calculating the oil film thickness of the blade top according to the oil film supporting force and the current structural parameter;

and comparing the thickness of the oil film with the roughness of the inner surfaces of the blades and the stator, and calculating a film thickness ratio parameter.

8. The method for designing structural parameters of a dual acting vane pump of claim 7 wherein,

the calculating the oil film thickness of the blade tip according to the oil film supporting force and the current structural parameter comprises the following steps:

calculating viscosity parameters and elasticity parameters from the oil film supporting force and the current structural parameters according to the following formula:

wherein g _e Representing the elastic parameter g _v Represents the viscosity parameter, eta ₀ The viscosity of the oil under normal pressure is W, the dynamic pressure supporting force of the oil between the blade and the stator on the blade is represented by W, the magnitude of the dynamic pressure supporting force can be obtained through stress analysis of the blade, U represents the entrainment speed between the blade and the surface of the stator, and the entrainment speed is approximately 0.5 times of the rotation speed of the input shaft;

represents the equivalent radius of curvature between the leaf and the stator surface, wherein R ₁ Represents the radius of curvature of the stator, R ₂ Representing the curvature radius of the blade, L representing the line contact length of the blade and the surface of the stator, alpha representing the viscosity-pressure coefficient of oil, E representing the equivalent elastic modulus between the blade and the surface of the stator;

taking the viscosity parameter and the elasticity parameter as coordinate parameters, and determining a current target state area of the coordinate parameters in a Hooke lubrication state diagram;

and calculating the thickness of the oil film at the top end of the blade according to the target state area.

9. The method for designing structural parameters of a dual acting vane pump of claim 8 wherein,

the calculating the oil film thickness of the blade tip according to the target state area comprises the following steps:

calculating the oil film thickness of the blade tip from the target state region according to:

wherein,,

indicating the oil film thickness of the blade tip when the target state region is R-I region,/-, is->

Indicating the oil film thickness of the blade tip when the target state region is R-V region,/->

Indicating the oil film thickness of the blade tip when the target state area is E-I area,/-, is->

Indicating the oil film thickness of the blade tip when the target state region is the E-V region.

10. The method for designing structural parameters of a dual acting vane pump of claim 7 wherein,

comparing the oil film thickness with the inner surface roughness of the blade and the stator, and calculating a film thickness ratio parameter, wherein the film thickness ratio parameter comprises:

the film thickness ratio parameter is calculated according to the following formula:

wherein λ represents a film thickness ratio parameter, h _min Representing the current bladeOil film thickness at tip Rα ₁ Indicating the roughness of the inner surface of the blade, rα ₂ Representing the roughness of the inner surface of the stator.

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