CN116620247B - Hydraulic retarder braking moment prediction method and device based on double pressure sensors - Google Patents

Hydraulic retarder braking moment prediction method and device based on double pressure sensors Download PDF

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Publication number
CN116620247B
CN116620247B CN202310885205.1A CN202310885205A CN116620247B CN 116620247 B CN116620247 B CN 116620247B CN 202310885205 A CN202310885205 A CN 202310885205A CN 116620247 B CN116620247 B CN 116620247B
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rotor
retarder
current
hydrodynamic retarder
pressure
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CN116620247A (en
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黄勇
于良耀
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Tsinghua University
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Tsinghua University
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T17/00—Component parts, details, or accessories of power brake systems not covered by groups B60T8/00, B60T13/00 or B60T15/00, or presenting other characteristic features
    • B60T17/18—Safety devices; Monitoring
    • B60T17/22—Devices for monitoring or checking brake systems; Signal devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T10/00—Control or regulation for continuous braking making use of fluid or powdered medium, e.g. for use when descending a long slope
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/72—Electric energy management in electromobility

Abstract

The application relates to the technical field of fluid machinery, in particular to a hydraulic retarder braking moment prediction method and device based on double pressure sensors, wherein the method comprises the following steps: the working parameters of the hydraulic retarder and the critical rotating speed of a rotor of the hydraulic retarder are obtained, a braking torque prediction expression of the hydraulic retarder is constructed, and the current control pressure in the oil tank, the current pressure in the float chamber and the current rotating speed of the rotor are input into the braking torque prediction expression to predict the current braking torque of the hydraulic retarder. According to the embodiment of the application, the prediction result of the braking torque in the actual working state can be obtained through the braking torque prediction expression based on the current pressure of the oil tank and the float chamber of the hydraulic retarder and in combination with the current rotor rotating speed, so that the dynamic real-time prediction of the braking torque of the hydraulic retarder in the full rotating speed range is realized, the accuracy and the reliability of the braking torque prediction of the hydraulic retarder are improved, and the application range is wider.

Description

Hydraulic retarder braking moment prediction method and device based on double pressure sensors
Technical Field
The application relates to the technical field of fluid machinery, in particular to a hydraulic retarder braking moment prediction method and device based on double pressure sensors.
Background
The hydraulic retarder converts kinetic energy of a vehicle into internal energy of liquid for emission by utilizing damping effect generated when the liquid flows, can be used as auxiliary braking equipment of a heavy vehicle, and reduces the possibility of accidents of the heavy vehicle caused by heat fading failure of a main braking system.
In the related art, a brake torque prediction expression of the hydraulic retarder is established on the basis of a similar principle, and a brake torque prediction value of the hydraulic retarder is obtained according to the obtained prediction expression, so that the hydraulic retarder can be used for developing a whole vehicle control strategy of a heavy vehicle provided with the hydraulic retarder, and theoretical support can be provided for iterative design and performance optimization of the hydraulic retarder.
However, in the related art, due to the requirement of the geometric similarity principle in the similarity principle, the prediction expression is only suitable for prediction when the working cavity of the hydrodynamic retarder is in a full-fluid-charge state, real-time measurement cannot be performed on dynamic change of the fluid-charge rate of the hydrodynamic retarder, a predicted value which accords with the actual working state of the hydrodynamic retarder is difficult to obtain, the application range of the prediction of the braking torque of the hydrodynamic retarder is shortened, the practicability is weak, and the problem needs to be solved.
Disclosure of Invention
The application provides a hydraulic retarder braking torque prediction method and device based on double pressure sensors, which are used for solving the problems that in the related art, due to the requirement of a geometric similarity principle in a similarity principle, a prediction expression is only suitable for prediction when a working cavity of the hydraulic retarder is in a full-filling-rate state, real-time measurement cannot be performed on dynamic change of the filling rate of the hydraulic retarder, a predicted value which accords with the actual working state of the hydraulic retarder is difficult to obtain, the application range of the hydraulic retarder braking torque prediction is shortened, the practicability is weaker and the like.
An embodiment of a first aspect of the present application provides a method for predicting braking torque of a hydraulic retarder based on dual pressure sensors, comprising the steps of: acquiring working parameters of a hydrodynamic retarder and a critical rotation speed of a rotor of the hydrodynamic retarder; constructing a braking torque prediction expression of the hydrodynamic retarder based on the working parameters and the critical rotor speed; the method comprises the steps of obtaining the current control pressure in an oil tank of the hydraulic retarder, the current pressure in a float chamber and the current rotor rotating speed, and inputting the current control pressure in the oil tank, the current pressure in the float chamber and the current rotor rotating speed into the braking torque prediction expression to predict the current braking torque of the hydraulic retarder.
Optionally, in an embodiment of the present application, the acquiring the working parameter of the hydrodynamic retarder and the critical rotational speed of the rotor of the hydrodynamic retarder includes: acquiring the outer diameter, the inner diameter and the blade inclination angle of a rotor of the hydrodynamic retarder, and calculating corresponding liquid flow angles at an oil inlet and an oil outlet according to the blade inclination angle of the rotor; and obtaining the density of the working oil in the oil tank.
Optionally, in an embodiment of the present application, the acquiring the working parameter of the hydrodynamic retarder and the critical rotational speed of the rotor of the hydrodynamic retarder includes: testing the hydrodynamic retarder to obtain a braking moment change curve and a float chamber pressure change curve of the hydrodynamic retarder; the rotor threshold speed is determined based on the bowl pressure change curve.
Optionally, in an embodiment of the present application, the constructing a braking torque prediction expression of the hydrodynamic retarder further includes: calculating a circumferential speed coefficient according to the critical rotation speed and the control pressure of the rotor, and estimating an impact loss coefficient; and optimizing and adjusting based on the circumferential speed coefficient and the impact loss coefficient to enable the braking torque prediction expression corresponding curve and the braking torque change curve to reach a preset fitting condition.
Optionally, in an embodiment of the present application, the predicted expression of the braking torque of the hydrodynamic retarder is:
wherein ,for the predicted braking torque value of the hydrodynamic retarder in the closed condition of the float chamber,/->For the predicted braking torque value of the hydrodynamic retarder with the float chamber open,/->For the current rotor speed,/->For the current control pressure in the tank, < > is>For the current pressure in the float chamber, < > is>For the density of the working oil in the tank, < >>For the impact loss coefficient, < >>For the outer diameter of the hydrodynamic retarder rotor, < > a->For the inner diameter of the hydrodynamic retarder rotor, < > is>For the corresponding flow angle at the oil inlet, +.>For the corresponding flow angle at the oil outlet, +.>Is the peripheral velocity coefficient.
An embodiment of the second aspect of the present application provides a hydraulic retarder braking torque prediction apparatus based on dual pressure sensors, including: the acquisition module is used for acquiring the working parameters of the hydraulic retarder and the critical rotation speed of the rotor of the hydraulic retarder; the construction module is used for constructing a braking torque prediction expression of the hydrodynamic retarder based on the working parameters and the critical rotating speed of the rotor; the prediction module is used for acquiring the current control pressure in the oil tank of the hydrodynamic retarder, the current pressure in the float chamber and the current rotor rotating speed, and inputting the current control pressure in the oil tank, the current pressure in the float chamber and the current rotor rotating speed into the braking moment prediction expression so as to predict the current braking moment of the hydrodynamic retarder.
Optionally, in one embodiment of the present application, the acquiring module includes: the first acquisition unit is used for acquiring the outer diameter, the inner diameter and the blade inclination angle of the rotor of the hydrodynamic retarder, and calculating corresponding liquid flow angles at the oil inlet and the oil outlet according to the blade inclination angle of the rotor; and the second acquisition unit is used for acquiring the density of the working oil in the oil tank.
Optionally, in one embodiment of the present application, the acquiring module includes: the testing unit is used for testing the hydraulic retarder and obtaining a braking moment change curve and a float chamber pressure change curve of the hydraulic retarder; and the confirming unit is used for confirming the critical rotating speed of the rotor based on the pressure change curve of the float chamber.
Optionally, in one embodiment of the present application, the building module includes: the calculating unit is used for calculating a circumferential speed coefficient according to the critical rotating speed of the rotor and the control pressure and estimating an impact loss coefficient; and the optimizing unit is used for optimizing and adjusting based on the circumferential speed coefficient and the impact loss coefficient, so that a preset fitting condition is achieved between the braking torque prediction expression corresponding curve and the braking torque change curve.
Optionally, in an embodiment of the present application, the predicted expression of the braking torque of the hydrodynamic retarder is:
wherein ,for the predicted braking torque value of the hydrodynamic retarder in the closed condition of the float chamber,/->For the predicted braking torque value of the hydrodynamic retarder with the float chamber open,/->For the current rotor speed,/->For the current control pressure in the tank, < > is>For the current pressure in the float chamber, < > is>For the density of the working oil in the tank, < >>For the impact loss coefficient, < >>For the outer diameter of the hydrodynamic retarder rotor, < > a->For the inner diameter of the hydrodynamic retarder rotor, < > is>For the corresponding flow angle at the oil inlet, +.>For the corresponding flow angle at the oil outlet, +.>Is the peripheral velocity coefficient.
An embodiment of a third aspect of the present application provides an electronic device, including: the hydraulic retarder braking moment prediction method based on the double pressure sensors comprises a memory, a processor and a computer program, wherein the computer program is stored in the memory and can run on the processor, and the processor executes the program to realize the hydraulic retarder braking moment prediction method based on the double pressure sensors.
An embodiment of a fourth aspect of the application provides a computer readable storage medium storing a computer program which when executed by a processor implements a method for predicting a braking torque of a hydrodynamic retarder based on dual pressure sensors as above.
According to the embodiment of the application, the prediction result of the braking torque in the actual working state can be obtained through the braking torque prediction expression based on the current pressure of the oil tank and the float chamber of the hydraulic retarder and in combination with the rotating speed of the rotor, so that the dynamic real-time prediction of the braking torque of the hydraulic retarder in the full rotating speed range is realized, the accuracy and the reliability of the braking torque prediction of the hydraulic retarder are improved, and the application range is wider. Therefore, the problems that in the related technology, due to the requirement of the geometric similarity principle in the similarity principle, a prediction expression is only suitable for prediction when the working cavity of the hydrodynamic retarder is in a full-filling-rate state, real-time measurement cannot be performed on dynamic change of the filling rate of the hydrodynamic retarder, a predicted value which accords with the actual working state of the hydrodynamic retarder is difficult to obtain, the application range of the prediction of the braking torque of the hydrodynamic retarder is shortened, the practicability is weak and the like are solved.
Additional aspects and advantages of the application will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the application.
Drawings
The foregoing and/or additional aspects and advantages of the application will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings, in which:
FIG. 1 is a flow chart of a hydraulic retarder braking torque prediction method based on dual pressure sensors according to an embodiment of the present application;
FIG. 2 is a schematic view of the vortex domain, velocity and pressure distribution of a liquid flow in a stator based on a Rankine combined vortex model according to an embodiment of the application;
FIG. 3 is a schematic structural diagram of a hydraulic retarder braking torque prediction system based on dual pressure sensors according to an embodiment of the present application;
FIG. 4 is a graphical representation of tank pressure and fuel bowl pressure as a function of rotational speed for a control pressure of 1.7bar in accordance with one embodiment of the present application;
FIG. 5 is a graph showing a comparison of predicted and experimental braking torque results at a control pressure of 1.7bar according to one embodiment of the present application;
FIG. 6 is a schematic diagram of error analysis of a predicted braking torque result at a control pressure of 1.7bar according to one embodiment of the present application;
FIG. 7 is a graph showing a comparison of predicted braking torque and experimental results at four different control pressures in accordance with one embodiment of the present application;
fig. 8 is a schematic structural diagram of a hydraulic retarder braking torque prediction device based on dual pressure sensors according to an embodiment of the present application;
fig. 9 is a schematic structural diagram of an electronic device according to an embodiment of the present application.
Detailed Description
Embodiments of the present application are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative and intended to explain the present application and should not be construed as limiting the application.
The method and the device for predicting the braking torque of the hydraulic retarder based on the double pressure sensors are described below with reference to the accompanying drawings. Aiming at the problems that in the related art mentioned in the background art, due to the requirement of the geometric similarity principle in the similarity principle, a prediction expression is only suitable for prediction in the state that the working cavity of the hydrodynamic retarder is full of the filling rate, real-time measurement cannot be carried out on dynamic change of the filling rate of the hydrodynamic retarder, a predicted value which accords with the actual working state of the hydrodynamic retarder is difficult to obtain, the application range of the prediction of the braking torque of the hydrodynamic retarder is shortened, and the practicability is weaker. Therefore, the problems that in the related technology, due to the requirement of the geometric similarity principle in the similarity principle, a prediction expression is only suitable for prediction when the working cavity of the hydrodynamic retarder is in a full-filling-rate state, real-time measurement cannot be performed on dynamic change of the filling rate of the hydrodynamic retarder, a predicted value which accords with the actual working state of the hydrodynamic retarder is difficult to obtain, the application range of the prediction of the braking torque of the hydrodynamic retarder is shortened, the practicability is weak and the like are solved.
Specifically, fig. 1 is a schematic flow chart of a hydraulic retarder braking moment prediction method based on a dual pressure sensor according to an embodiment of the present application.
As shown in fig. 1, the hydraulic retarder braking torque prediction method based on the double pressure sensors comprises the following steps:
in step S101, an operating parameter of the hydrodynamic retarder and a critical rotational speed of a rotor of the hydrodynamic retarder are obtained.
It will be appreciated that in embodiments of the present application, the operating parameters of the hydrodynamic retarder may be parameters related to the actual operation of the components in the hydrodynamic retarder, including, but not limited to, the dimensional parameters of the components in the hydrodynamic retarder, the flow parameters of the components in the hydrodynamic retarder during the actual operation, etc. The critical rotational speed of the rotor may be the critical rotational speed of the hydrodynamic retarder rotor when the pressure in the float chamber of the hydrodynamic retarder is 0.
Optionally, in an embodiment of the present application, obtaining the working parameter of the hydrodynamic retarder and the critical rotational speed of the rotor of the hydrodynamic retarder comprises: acquiring the outer diameter, the inner diameter and the blade inclination angle of a rotor of the hydrodynamic retarder, and calculating corresponding liquid flow angles at an oil inlet and an oil outlet according to the blade inclination angle of the rotor; and obtaining the density of the working oil in the oil tank.
In the actual working process, the outer diameter of the hydrodynamic retarder rotor can be obtained by measuring or based on the original size data of the hydrodynamic retarderInner diameter->According to rotor blade pitch->Calculating the corresponding flow angle at the oil inlet>And the corresponding flow angle at the oil outlet>And the density of the working oil in the oil tank is obtained>The method is used for the process of acquiring the critical rotation speed of the rotor of the hydrodynamic retarder in the following steps.
Optionally, in an embodiment of the present application, obtaining the working parameter of the hydrodynamic retarder and the critical rotational speed of the rotor of the hydrodynamic retarder comprises: testing the hydrodynamic retarder to obtain a braking moment change curve of the hydrodynamic retarder and a pressure change curve of a float chamber; based on the bowl pressure change curve, a rotor threshold speed is determined.
In some embodiments, the hydraulic retarder may be bench tested by a test bench, fixing the control pressure in the tankThe braking torque of the hydrodynamic retarder is acquired at this point +.>And pressure in the bowl->Obtaining critical rotation speed ++when the pressure of the float chamber is 0 according to the change curve of the rotation speed of the rotor>So as to further realize the construction of the predicted expression of the braking torque of the hydrodynamic retarder in the following steps.
In step S102, a braking torque prediction expression of the hydrodynamic retarder is constructed based on the operating parameters and the critical rotational speed of the rotor.
It can be understood that in the embodiment of the application, the construction of the braking torque prediction expression of the hydrodynamic retarder can be performed based on the working parameters and the critical rotation speed of the rotor obtained in the steps and on the hydrodynamics theory and the Rankine combined vortex model, so as to obtain the braking torque prediction expression conforming to the actual working condition of the hydrodynamic retarder.
Optionally, in an embodiment of the application, the predicted expression of the braking torque of the hydrodynamic retarder is:
wherein ,for the predicted braking torque value of the hydrodynamic retarder in the closed float chamber +.>For the predicted braking torque value of the hydrodynamic retarder with the float chamber open,/for the hydraulic retarder>For the current rotor speed,/->For the current control pressure in the tank,for the current pressure in the bowl, +.>Is the density of working oil in the oil tank, +.>For the impact loss coefficient>Is the outer diameter of the rotor of the hydrodynamic retarder +.>Is the inner diameter of the rotor of the hydrodynamic retarder +.>Is the corresponding liquid flow angle at the oil inlet +.>For the corresponding flow angle at the oil outlet, +.>Is a peripheral velocity coefficient.
Specifically, a Rankine combined vortex model may be introduced to describe the vortex motion of the oil in the stator as shown in fig. 2, where fig. 2 (a) identifies the vortex motion in the hydrodynamic retarder stator, the inner semicircular region representing oil or air and the outer semicircular region representing oil. Based on the characteristics of the hydraulic retarder structure and the Rankine combined model, as shown in the pressure distribution in the vortex of the figure 2 (c), the pressure at the infinite distance in the Rankine combined model can be obtainedNamely the control pressure in the hydraulic retarder tank>. Introduction parameter->Describing the positions of the oil inlet and the oil outlet of the fluid flow in the rotor, the values 1, 2,/-can be taken>Is 1 time represents the oil inlet of the liquid flow in the rotor, < >>The oil outlet of the liquid flow in the rotor is represented by time 2.
When the rotor rotation speed is low and the float chamber is in a closed state, the pressure at the center of the vortex flowEqual to the pressure in the float chamberAs shown in the velocity profile of the vortex in FIG. 2 (b), the vortex velocity at the interface of the forced vortex domain and the free vortex domain can be obtained>The method comprises the following steps:
wherein ,for the vortex speed at the interface of the forced vortex domain and the free vortex domain when the float chamber is in closed state, +.>For the current control pressure in the tank, +.>For the current pressure in the bowl, +.>Is the density of the working oil in the oil tank.
When the rotor rotation speed is higher, the internal pressure of the working cavity of the hydraulic retarder is reduced to be close to the external atmospheric pressure, the float chamber is opened, the internal of the working cavity is communicated with the external atmospheric pressure, and a cavity is gradually formed in the middle of the working cavity. At this time, the minimum pressure in the vortex domainEqual to the external atmospheric pressure->The vortex speeds at the interface of the forced and free vortex domains are thus obtained as:
wherein ,for the vortex speed at the interface of the forced vortex domain and the free vortex domain when the float chamber is in the open state, +.>For the current control pressure in the tank, +.>Is the density of the working oil in the oil tank.
Peripheral speed of rotor at oil inlet and oil outletThe method comprises the following steps:
wherein ,for the current rotor speed,/->Is the flow channel outer diameter parameter of the liquid flow at the oil inlet and the oil outlet in the rotor. From the speed triangle relationship in the hydrodynamics, the vortex speed in the rotor can be established>Rotor peripheral speed->The circumferential circulation speed of oil liquid>The relation between the two is:
wherein ,for the vortex speed at the interface of the forced vortex domain and the free vortex domain +.>For the corresponding flow angle at the oil inlet and at the oil outlet, < >>For the peripheral speed of the rotor at the oil inlet and at the oil outlet, < >>Is the circumferential circulation speed of the oil. Introducing a peripheral velocity coefficient->Establishing the rotor peripheral speed +.>The circumferential circulation speed of oil liquid>The relation between:
wherein ,for the peripheral speed of the rotor at the oil inlet and at the oil outlet, < >>Is a peripheral velocity coefficient>Is the circumferential circulation speed of the oil. Further introducing an impact loss coefficient->Characterizing oil circumferential speed>Impact loss when flowing between the stator and the rotor. By combining the principle that the cross-sectional areas of the through-flow are equal, the flow channel external diameter parameters of the liquid flow at the oil inlet and the oil outlet in the rotor can be determined>And circulation flow in the working chamber:
wherein ,for circulating the flow in the rotor working chamber, < >>For the flow channel outer diameter parameters of the liquid flow at the oil inlet and the oil outlet in the rotor, < >>For the flow channel inner diameter parameters of the liquid flow at the oil inlet and the oil outlet in the rotor +.>Is the average vortex speed on the cross section of the flow. Finally, the equation of Euler turbine:
wherein ,for the braking torque of the hydrodynamic retarder, +.>Is the density of working oil in the oil tank, +.>For circulating the flow in the rotor working chamber, < >>Is the circumferential circulation speed of oil liquid at the oil outlet>For the flow channel outer diameter parameter of the liquid flow in the rotor oil outlet, < >>Is the circumferential circulation speed of the oil liquid at the oil inlet, < + >>Is the flow channel outer diameter parameter of the liquid flow in the rotor oil inlet. At this time, a braking torque expression of the hydrodynamic retarder may be established:
wherein ,for the predicted braking torque value of the hydrodynamic retarder in the closed float chamber +.>For the predicted braking torque value of the hydrodynamic retarder with the float chamber open,/for the hydraulic retarder>For the current rotor speed,/->For the current control pressure in the tank,for the current pressure in the bowl, +.>Is the density of working oil in the oil tank, +.>For the impact loss coefficient>Is the outer diameter of the rotor of the hydrodynamic retarder +.>Is the inner diameter of the rotor of the hydrodynamic retarder +.>Is the corresponding liquid flow angle at the oil inlet +.>For the corresponding flow angle at the oil outlet, +.>Is a peripheral velocity coefficient.
In the above-mentioned method, when the rotating speed of rotor is low, the float chamber is closed, its internal pressure is greater than external atmospheric pressure) Braking moment of hydrodynamic retarder>The analytical expression of (2) is:
wherein ,。
when the rotating speed of the rotor is higher, the float chamber is opened, and the internal pressure is equal to the external atmospheric pressure) During this time, the hydrodynamic retarder braking torque +.>The analytical expression of (2) is:
，
wherein ,-/>the method comprises the following steps of:
。
optionally, in an embodiment of the present application, constructing a predicted expression of a braking torque of the hydrodynamic retarder further comprises: calculating a circumferential speed coefficient according to the critical rotation speed and the control pressure of the rotor, and estimating an impact loss coefficient; and carrying out optimization adjustment based on the circumferential speed coefficient and the impact loss coefficient, so that a preset fitting condition is achieved between a corresponding curve of the brake torque prediction expression and a brake torque change curve.
In the actual working process, the peripheral speed coefficientThe circumferential velocity coefficient +.>：
wherein ,for the current control pressure in the tank, +.>For the corresponding flow angle at the oil outlet, +.>The critical rotation speed of the rotor is the outer diameter of the rotor of the hydrodynamic retarder,>is the inner diameter of the rotor of the hydrodynamic retarder +.>Is the density of the working oil in the oil tank. For a hydrodynamic retarder, the impact loss coefficient +.>Usually around 0.3, can be achieved by fine tuning +.> and />And (3) the numerical value is further close to and overlapped with the braking moment curve obtained by the prediction expression and the braking moment change curve obtained based on the test in the process, so that a specific expression of the braking moment prediction method of the hydrodynamic retarder can be obtained.
In step S103, the current control pressure in the tank of the hydrodynamic retarder, the current pressure in the float chamber and the current rotor speed are obtained, and the current control pressure in the tank, the current pressure in the float chamber and the current rotor speed are input into a braking torque prediction expression to predict the current braking torque of the hydrodynamic retarder.
It is understood that in the embodiment of the application, the current control pressure in the oil tank of the hydraulic retarder can be acquired through the pressure sensor on the oil cavity, the current pressure in the float chamber can be acquired through the pressure sensor on the float chamber, the current rotor rotating speed of the hydraulic retarder can be acquired in real time through the CAN (Controller Area Network) bus, and the current control pressure is input into the brake torque prediction expression obtained in the step to acquire the current brake torque of the predicted hydraulic retarder in real time.
The working of the embodiments of the present application will be described in detail below with reference to fig. 3-7.
Specifically, as shown in fig. 3, a structural schematic diagram of a hydraulic retarder braking torque prediction system based on a dual pressure sensor according to an embodiment of the present application. The method comprises the following steps: stator 301, input shaft 302, rotor 303, fuel bowl 304, fuel tank 305, heat exchanger 306, control valve 307, in-oil chamber pressure sensor 308, in-bowl pressure sensor 309, hydrodynamic retarder controller 310, vehicle chassis CAN network 311, and hydrodynamic retarder 30.
Firstly, the hydrodynamic retarder 30 is measured to obtain the outer diameter R, the inner diameter R and the inclination angle of the bladesFlow angle at the rotor oil inlet and oil outlet> and />Density of oil>See in particular table 1, which is a table of parameters relevant to the hydrodynamic retarder test.
TABLE 1
On the bench to feed the hydrodynamic retarder 30Line control pressureExternal characteristic test during this time, and at the same time the control pressure +_of the tank 305 is detected by the pressure sensor>And the pressure of the float chamber 304->According to the rotor speed->Is a change curve of (2); as the rotational speed->Elevated when the pressure of the float chamber 304 +.>The critical rotational speed is approximately ± at the time of>See fig. 4 for a plot of control pressure of the tank 305 and pressure of the float chamber 304 as a function of rotational speed for a control pressure of 1.7 bar.
Preliminarily determining a peripheral speed coefficient by a formula:，/>. At this time, the experimental result and model prediction result of the braking moment and the error distribution are respectively shown in fig. 5 and 6, and it is known that the overlap ratio of the braking moment prediction result and the experimental result is better, and the average error is-8.8%. Therefore, the specific expression of the braking torque prediction method of the hydraulic retarder is as follows:
when the rotation speed isThe float chamber 304 is closed and its internal pressure is greater than the external atmospheric pressure ()>) When the hydraulic retarder is used, the predicted braking moment value is as follows:
when the rotation speed isThe float chamber 304 is opened and its internal pressure is equal to the external atmospheric pressure (+)>) When the hydraulic retarder is used, the predicted braking moment value is as follows:
，
in the above formula:
wherein ,/>Is a predicted value of the braking torque of the hydrodynamic retarder under the condition that the float chamber is closed,for the predicted braking torque value of the hydrodynamic retarder with the float chamber open,/for the hydraulic retarder>For the current rotor speed,/->For the current control pressure in the tank, +.>Is the current pressure in the float chamber.
Pressure control of the hydrodynamic retarder is achieved through the two types of hydraulic retardersThe brake torques under four conditions of 2.8bar, 2.2bar, 1.4bar and 0.6bar are respectively predicted, the predicted results and the brake torques measured by an actual rack are shown in figure 6, and the average errors under the four conditions are 6.3%,9.5%,11.8% and 4.2%, so that the effectiveness of the method provided by the application is verified.
According to the hydraulic retarder braking moment prediction method based on the double pressure sensors, the prediction result of the braking moment in the actual working state can be obtained through the braking moment prediction expression based on the current pressures of the oil tank and the float chamber of the hydraulic retarder and the rotor rotating speed, so that the dynamic real-time prediction of the braking moment of the hydraulic retarder in the full rotating speed range is realized, the accuracy and the reliability of the braking moment prediction of the hydraulic retarder are improved, and the application range is wider. Therefore, the problems that in the related technology, due to the requirement of the geometric similarity principle in the similarity principle, a prediction expression is only suitable for prediction when the working cavity of the hydrodynamic retarder is in a full-filling-rate state, real-time measurement cannot be performed on dynamic change of the filling rate of the hydrodynamic retarder, a predicted value which accords with the actual working state of the hydrodynamic retarder is difficult to obtain, the application range of the prediction of the braking torque of the hydrodynamic retarder is shortened, the practicability is weak and the like are solved.
The hydraulic retarder braking moment prediction device based on the double pressure sensors according to the embodiment of the application is described with reference to the accompanying drawings.
Fig. 8 is a schematic structural diagram of a hydraulic retarder braking torque prediction device based on dual pressure sensors according to an embodiment of the present application.
As shown in fig. 8, the hydraulic retarder braking torque prediction apparatus 10 based on the dual pressure sensor includes: an acquisition module 100, a construction module 200 and a prediction module 300.
The acquisition module 100 is configured to acquire an operating parameter of the hydrodynamic retarder and a critical rotational speed of a rotor of the hydrodynamic retarder.
The construction module 200 is configured to construct a braking torque prediction expression of the hydrodynamic retarder based on the operating parameter and the critical rotational speed of the rotor.
The prediction module 300 is configured to obtain a current control pressure in a tank of the hydrodynamic retarder, a current pressure in a float chamber, and a current rotor rotational speed, and input the current control pressure in the tank, the current pressure in the float chamber, and the current rotor rotational speed into a braking torque prediction expression to predict a current braking torque of the hydrodynamic retarder.
Optionally, in one embodiment of the present application, the acquiring module 100 includes: a first acquisition unit and a second acquisition unit.
The first acquisition unit is used for acquiring the outer diameter, the inner diameter and the blade inclination angle of the rotor of the hydrodynamic retarder, and calculating corresponding liquid flow angles at the oil inlet and the oil outlet according to the blade inclination angle of the rotor.
And the second acquisition unit is used for acquiring the density of the working oil in the oil tank.
Optionally, in one embodiment of the present application, the acquiring module 100 includes: a test module and a validation module.
The testing unit is used for testing the hydrodynamic retarder and obtaining a braking moment change curve of the hydrodynamic retarder and a pressure change curve of the float chamber.
And the confirmation unit is used for determining the critical rotating speed of the rotor of the hydrodynamic retarder based on the pressure change curve of the float chamber.
Optionally, in one embodiment of the present application, the building block 200 includes: a calculation unit and an optimization unit.
And the calculating unit is used for calculating a circumferential speed coefficient according to the critical rotating speed of the rotor and the control pressure and acquiring an impact loss coefficient.
The optimization unit is used for performing optimization adjustment based on the circumferential speed coefficient and the impact loss coefficient, so that the corresponding curve of the braking moment prediction expression and the braking moment change curve reach preset fitting conditions.
Optionally, in an embodiment of the application, the predicted expression of the braking torque of the hydrodynamic retarder is:
wherein ,for the predicted braking torque value of the hydrodynamic retarder in the closed float chamber +.>For the predicted braking torque value of the hydrodynamic retarder with the float chamber open,/for the hydraulic retarder>For the current rotor speed,/->For the current control pressure in the tank,for the current pressure in the bowl, +.>Is the density of working oil in the oil tank, +.>For the impact loss coefficient>Is the outer diameter of the rotor of the hydrodynamic retarder +.>Is the inner diameter of the rotor of the hydrodynamic retarder +.>Is the corresponding liquid flow angle at the oil inlet +.>For the corresponding flow angle at the oil outlet, +.>Is a peripheral velocity coefficient.
It should be noted that the foregoing explanation of the embodiment of the method for predicting the braking torque of the hydraulic retarder based on the dual pressure sensor is also applicable to the device for predicting the braking torque of the hydraulic retarder based on the dual pressure sensor of the embodiment, and will not be repeated herein.
According to the hydraulic retarder braking moment prediction device based on the double pressure sensors, the prediction result of the braking moment in the actual working state can be obtained through the braking moment prediction expression based on the current pressure of the oil tank and the float chamber of the hydraulic retarder and the rotor rotating speed, so that the dynamic real-time prediction of the braking moment of the hydraulic retarder in the full rotating speed range is realized, the accuracy and the reliability of the braking moment prediction of the hydraulic retarder are improved, and the application range is wider. Therefore, the problems that in the related technology, due to the requirement of the geometric similarity principle in the similarity principle, a prediction expression is only suitable for prediction when the working cavity of the hydrodynamic retarder is in a full-filling-rate state, real-time measurement cannot be performed on dynamic change of the filling rate of the hydrodynamic retarder, a predicted value which accords with the actual working state of the hydrodynamic retarder is difficult to obtain, the application range of the prediction of the braking torque of the hydrodynamic retarder is shortened, the practicability is weak and the like are solved.
Fig. 9 is a schematic structural diagram of an electronic device according to an embodiment of the present application. The electronic device may include:
memory 901, processor 902, and a computer program stored on memory 901 and executable on processor 902.
The processor 902 implements the hydraulic retarder braking torque prediction method based on the dual pressure sensors provided in the above embodiments when executing a program.
Further, the electronic device further includes:
a communication interface 903 for communication between the memory 901 and the processor 902.
Memory 901 for storing a computer program executable on processor 902.
Memory 901 may comprise high-speed RAM memory or may also include non-volatile memory (non-volatile memory), such as at least one disk memory.
If the memory 901, the processor 902, and the communication interface 903 are implemented independently, the communication interface 903, the memory 901, and the processor 902 may be connected to each other through a bus and perform communication with each other. The bus may be an industry standard architecture (Industry Standard Architecture, abbreviated ISA) bus, an external device interconnect (Peripheral Component, abbreviated PCI) bus, or an extended industry standard architecture (Extended Industry Standard Architecture, abbreviated EISA) bus, among others. The buses may be divided into address buses, data buses, control buses, etc. For ease of illustration, only one thick line is shown in fig. 9, but not only one bus or one type of bus.
Alternatively, in a specific implementation, if the memory 901, the processor 902, and the communication interface 903 are integrated on a chip, the memory 901, the processor 902, and the communication interface 903 may communicate with each other through internal interfaces.
The processor 902 may be a central processing unit (Central Processing Unit, abbreviated as CPU) or an application specific integrated circuit (Application Specific Integrated Circuit, abbreviated as ASIC) or one or more integrated circuits configured to implement embodiments of the present application.
The present embodiment also provides a computer readable storage medium having stored thereon a computer program which when executed by a processor implements the hydraulic retarder braking torque prediction method based on dual pressure sensors as above.
In the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present application. In this specification, schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or N embodiments or examples. Furthermore, the different embodiments or examples described in this specification and the features of the different embodiments or examples may be combined and combined by those skilled in the art without contradiction.
Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In the description of the present application, "N" means at least two, for example, two, three, etc., unless specifically defined otherwise.
Any process or method descriptions in flow charts or otherwise described herein may be understood as representing modules, segments, or portions of code which include one or more executable instructions for implementing specific logical functions or steps of the process, and additional implementations are included within the scope of the preferred embodiment of the present application in which functions may be executed out of order from that shown or discussed, including substantially concurrently or in reverse order from that shown or discussed, depending on the functionality involved, as would be understood by those reasonably skilled in the art of the embodiments of the present application.
Logic and/or steps represented in the flowcharts or otherwise described herein, e.g., a ordered listing of executable instructions for implementing logical functions, can be embodied in any computer-readable medium for use by or in connection with an instruction execution system, apparatus, or device, such as a computer-based system, processor-containing system, or other system that can fetch the instructions from the instruction execution system, apparatus, or device and execute the instructions. For the purposes of this description, a "computer-readable medium" can be any means that can contain, store, communicate, propagate, or transport the program for use by or in connection with the instruction execution system, apparatus, or device. More specific examples (a non-exhaustive list) of the computer-readable medium would include the following: an electrical connection (electronic device) having one or N wires, a portable computer cartridge (magnetic device), a Random Access Memory (RAM), a read-only memory (ROM), an erasable programmable read-only memory (EPROM or flash memory), an optical fiber device, and a portable compact disc read-only memory (CDROM). In addition, the computer readable medium may even be paper or other suitable medium on which the program is printed, as the program may be electronically captured, via optical scanning of the paper or other medium, then compiled, interpreted or otherwise processed in a suitable manner if necessary, and then stored in a computer memory.
It is to be understood that portions of the present application may be implemented in hardware, software, firmware, or a combination thereof. In the above-described embodiments, the N steps or methods may be implemented in software or firmware stored in a memory and executed by a suitable instruction execution system. As with the other embodiments, if implemented in hardware, may be implemented using any one or combination of the following techniques, as is well known in the art: discrete logic circuits having logic gates for implementing logic functions on data signals, application specific integrated circuits having suitable combinational logic gates, programmable Gate Arrays (PGAs), field Programmable Gate Arrays (FPGAs), and the like.
Those of ordinary skill in the art will appreciate that all or a portion of the steps carried out in the method of the above-described embodiments may be implemented by a program to instruct related hardware, where the program may be stored in a computer readable storage medium, and where the program, when executed, includes one or a combination of the steps of the method embodiments.
In addition, each functional unit in the embodiments of the present application may be integrated in one processing module, or each unit may exist alone physically, or two or more units may be integrated in one module. The integrated modules may be implemented in hardware or in software functional modules. The integrated modules may also be stored in a computer readable storage medium if implemented in the form of software functional modules and sold or used as a stand-alone product.
The above-mentioned storage medium may be a read-only memory, a magnetic disk or an optical disk, or the like. While embodiments of the present application have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the application, and that variations, modifications, alternatives and variations may be made to the above embodiments by one of ordinary skill in the art within the scope of the application.

Claims (4)

1. The hydraulic retarder braking moment prediction method based on the double pressure sensors is characterized by comprising the following steps of:
the method for obtaining the working parameters of the hydraulic retarder and the critical rotation speed of the rotor of the hydraulic retarder comprises the following steps of: acquiring the outer diameter, the inner diameter and the blade inclination angle of a rotor of the hydrodynamic retarder, calculating corresponding liquid flow angles at an oil inlet and an oil outlet according to the blade inclination angle of the rotor, acquiring the density of working oil in an oil tank, testing the hydrodynamic retarder, acquiring a braking moment change curve and a float chamber pressure change curve of the hydrodynamic retarder, and determining the critical rotating speed of the rotor based on the float chamber pressure change curve;
based on the working parameters and the critical rotation speed of the rotor, constructing a braking moment prediction expression of the hydrodynamic retarder, wherein the constructing the braking moment prediction expression of the hydrodynamic retarder comprises: calculating a circumferential speed coefficient according to the critical rotation speed of the rotor and the control pressure, estimating an impact loss coefficient, and carrying out optimization adjustment based on the circumferential speed coefficient and the impact loss coefficient to enable a braking moment prediction expression corresponding curve and a braking moment change curve to reach a preset fitting condition, wherein the braking moment prediction expression of the hydraulic retarder is as follows:
wherein ,for the predicted braking torque value of the hydrodynamic retarder in the closed condition of the float chamber,/->For the predicted braking torque value of the hydrodynamic retarder with the float chamber open,/->For the current rotor speed,/->For the current control pressure in the tank, < > is>For the current pressure in the float chamber, < > is>For the density of the working oil in the tank, < >>For the impact loss coefficient, < >>For the outer diameter of the hydrodynamic retarder rotor, < > a->For the inner diameter of the hydrodynamic retarder rotor, < > is>For the corresponding flow angle at the oil inlet, +.>For the corresponding flow angle at the oil outlet, +.>Is the peripheral velocity coefficient; and
the method comprises the steps of obtaining the current control pressure in the oil tank of the hydraulic retarder, the current pressure in the float chamber and the current rotor rotating speed, and inputting the current control pressure in the oil tank, the current pressure in the float chamber and the current rotor rotating speed into the braking moment prediction expression so as to predict the current braking moment of the hydraulic retarder.
2. The utility model provides a hydraulic retarber braking moment prediction unit based on two pressure sensor which characterized in that includes:
the acquisition module is used for acquiring the working parameters of the hydraulic retarder and the critical rotation speed of the rotor of the hydraulic retarder, wherein the acquisition of the working parameters of the hydraulic retarder and the critical rotation speed of the rotor of the hydraulic retarder comprises the following steps: acquiring the outer diameter, the inner diameter and the blade inclination angle of a rotor of the hydrodynamic retarder, calculating corresponding liquid flow angles at an oil inlet and an oil outlet according to the blade inclination angle of the rotor, acquiring the density of working oil in an oil tank, testing the hydrodynamic retarder, acquiring a braking moment change curve and a float chamber pressure change curve of the hydrodynamic retarder, and determining the critical rotating speed of the rotor based on the float chamber pressure change curve;
the construction module is configured to construct a braking torque prediction expression of the hydrodynamic retarder based on the working parameter and the critical rotor speed, where the constructing the braking torque prediction expression of the hydrodynamic retarder includes: calculating a circumferential speed coefficient according to the critical rotation speed of the rotor and the control pressure, estimating an impact loss coefficient, and carrying out optimization adjustment based on the circumferential speed coefficient and the impact loss coefficient to enable a braking moment prediction expression corresponding curve and a braking moment change curve to reach a preset fitting condition, wherein the braking moment prediction expression of the hydraulic retarder is as follows:
wherein ,for the predicted braking torque value of the hydrodynamic retarder in the closed condition of the float chamber,/->For the predicted braking torque value of the hydrodynamic retarder with the float chamber open,/->For the current rotor speed,/->For the current control pressure in the tank, < > is>For the current pressure in the float chamber, < > is>For the density of the working oil in the tank, < >>For the impact loss coefficient, < >>For the outer diameter of the hydrodynamic retarder rotor, < > a->For the inner diameter of the hydrodynamic retarder rotor, < > is>For the corresponding flow angle at the oil inlet, +.>For the corresponding flow angle at the oil outlet, +.>Is the peripheral velocity coefficient; and
the prediction module is used for acquiring the current control pressure in the oil tank of the hydraulic retarder, the current pressure in the float chamber and the current rotor rotating speed, and inputting the current control pressure in the oil tank, the current pressure in the float chamber and the current rotor rotating speed into the braking moment prediction expression so as to predict the current braking moment of the hydraulic retarder.
3. An electronic device, comprising: a memory, a processor and a computer program stored on the memory and executable on the processor, the processor executing the program to implement the dual pressure sensor based hydraulic retarder braking torque prediction method as claimed in claim 1.
4. A computer readable storage medium having stored thereon a computer program, characterized in that the program is executed by a processor for implementing a dual pressure sensor based hydraulic retarder braking torque prediction method according to claim 1.
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