CN114962236A - Control method, device and system for torque compensation of variable displacement compressor - Google Patents

Control method, device and system for torque compensation of variable displacement compressor Download PDF

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Publication number
CN114962236A
CN114962236A CN202210669285.2A CN202210669285A CN114962236A CN 114962236 A CN114962236 A CN 114962236A CN 202210669285 A CN202210669285 A CN 202210669285A CN 114962236 A CN114962236 A CN 114962236A
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China
Prior art keywords
torque compensation
compressor
time
steady
dynamic
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Inventor
王健强
王桂洋
安泽伟
王建勇
张广军
王谦
陈国栋
赵弘志
闫朝亮
康洪升
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FAW Group Corp
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FAW Group Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • 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
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Abstract

The invention discloses a control method, a device and a system for torque compensation of a variable displacement compressor, wherein the method comprises the following steps: acquiring a steady-state operation parameter table, a dynamic operation parameter table and a filtering time table according to an automobile engine pedestal and an entire automobile test; acquiring real-time running parameters of the automobile; inquiring the steady-state operation parameter table according to the real-time operation parameters to determine the steady-state torque compensation value; inquiring the dynamic operation parameter table according to the real-time operation parameters to determine the dynamic torque compensation value; querying the filtering schedule according to the real-time operating parameters to determine a torque filtering time; determining a real-time torque compensation value according to the steady-state torque compensation value, the dynamic torque compensation value and the torque filtering time; and adjusting the output torque of the engine according to the real-time torque compensation value. The scheme of the invention can improve the control accuracy of the torque compensation of the variable displacement compressor and reduce the noise and vibration of the engine, thereby improving the driving comfort.

Description

Control method, device and system for torque compensation of variable displacement compressor
Technical Field
The embodiment of the invention relates to an automobile control technology, in particular to a control method, a device and a system for torque compensation of a variable displacement compressor.
Background
Air conditioning refrigeration systems have become an integral part of modern automobiles. The air conditioner compressor plays a role in compressing and delivering refrigerant vapor and is a core component of an air conditioner refrigeration system. The running state of the device directly influences the comfort and the dynamic property of the whole vehicle.
The compressor is one of the important loads of the engine. In order to reduce the influence of the compressor load on the engine speed, the engine electronic control system needs to perform torque compensation on the compressor load. The conventional control method for the torque compensation of the compressor directly utilizes a torque map to obtain a current torque value, and the method is high in speed and convenient to implement.
However, as the demand of users for vehicles increases, the conventional control method for torque compensation of the compressor can no longer meet the demand of users due to low accuracy. Particularly, the dynamic and steady state working condition conversion from the suction moment of the air conditioner compressor to the steady operation needs smoother transition, and the traditional control method for the torque compensation of the compressor cannot meet the requirement.
Disclosure of Invention
The invention provides a control method, a device and a system for torque compensation of a variable displacement compressor, which are used for improving the control accuracy of the torque compensation of the compressor, reducing the noise and vibration of an engine and improving the driving comfort.
In a first aspect, an embodiment of the present invention provides a control method for torque compensation of an automotive variable displacement compressor, including:
according to an automobile engine pedestal and an entire automobile test, a steady-state operation parameter table, a dynamic operation parameter table and a filtering time table are obtained, wherein the steady-state operation parameter table can show the relation between a steady-state torque compensation value and an operation parameter in a steady-state operation state, the dynamic operation parameter table can show the relation between the dynamic torque compensation value and the operation parameter in the steady-state operation state, and the filtering time table can show the relation between filtering time and the operation parameter;
acquiring real-time running parameters of the automobile;
inquiring the steady-state operation parameter table according to the real-time operation parameters to determine the steady-state torque compensation value;
inquiring the dynamic operation parameter table according to the real-time operation parameters to determine the dynamic torque compensation value;
querying the filtering time table according to the real-time operation parameters to determine torque filtering time;
determining a real-time torque compensation value according to the steady-state torque compensation value, the dynamic torque compensation value and the torque filtering time;
and adjusting the output torque of the engine according to the real-time torque compensation value.
Optionally, the operating parameters include engine speed, compressor pressure value, compressor displacement, and compressor inlet air temperature.
Optionally, the steady state operation parameter table includes a first steady state table, a second steady state table, and a third steady state table;
according to the automobile engine rack and the whole automobile test, obtain steady state operation parameter table, dynamic operation parameter table and filtering time table, include:
according to the automobile engine pedestal and the whole automobile test, the relation between the steady-state torque compensation value and the compressor pressure value under the condition of each engine rotating speed is obtained, and the first steady-state table is generated, wherein the first steady-state table comprises the engine rotating speed and the compressor pressureA value, and a steady state predicted torque value M at a corresponding engine speed and a corresponding compressor pressure value 1 ；
According to the automobile engine rack and the whole automobile test, the relation between the steady-state torque compensation value and the compressor displacement under the condition of each engine speed is obtained, and the second steady-state table is generated, wherein the second steady-state table comprises the engine speed, the compressor displacement and a first displacement coefficient k under the condition of corresponding to the engine speed and the compressor displacement 1 ；
According to the automobile engine pedestal and the whole automobile test, acquiring the relation between the steady-state torque compensation value and the compressor air inlet temperature under each engine rotating speed condition, and generating a third steady-state table, wherein the third steady-state table comprises the engine rotating speed, the compressor air inlet temperature and a first temperature coefficient M under the condition of corresponding engine rotating speed and corresponding compressor air inlet temperature 2 。
Optionally, the dynamic operation parameter table includes a first dynamic table, a second dynamic table, and a third dynamic table;
according to the automobile engine rack and the whole automobile test, obtain steady state operation parameter table, dynamic operation parameter table and filtering time table, include:
according to the automobile engine pedestal and the whole automobile test, the relation between the dynamic torque compensation value and the compressor pressure value under each engine rotating speed condition is obtained, and the first dynamic table is generated, wherein the first dynamic table comprises the engine rotating speed, the compressor pressure value and the dynamic pre-estimated torque peak value M under the condition of corresponding engine rotating speed and corresponding compressor pressure value 3 ；
According to the automobile engine rack and the whole automobile test, the relation between the dynamic torque compensation value and the compressor displacement under the condition of each engine speed is obtained, and the second dynamic table is generated, wherein the second dynamic table comprises the engine speed, the compressor displacement and a second displacement coefficient k under the condition of corresponding to the engine speed and the compressor displacement 2 ；
Obtaining the rotating speed of each engine according to the test of the automobile engine pedestal and the whole automobileA relation between the dynamic torque compensation value and the compressor inlet air temperature under the condition, and generating the third dynamic table, wherein the third dynamic table comprises the engine rotating speed, the compressor inlet air temperature and a second temperature coefficient M under the condition of corresponding engine rotating speed and corresponding compressor inlet air temperature 4 。
Optionally, querying the steady state operating parameter table according to the real time operating parameter to determine the steady state torque compensation value comprises:
inquiring the steady state operation parameter table according to the real time operation parameters to obtain a steady state estimated torque value M corresponding to the real time operation parameters 1 First coefficient of displacement k 1 And a first temperature coefficient M 2 ；
Calculating the steady-state torque compensation value M according to a first formula W The first formula is M W ＝M 1 *k 1 +M 2 。
Optionally, querying the dynamic operating parameter table according to the real-time operating parameter to determine the dynamic torque compensation value comprises:
inquiring the dynamic operation parameter table according to the real-time operation parameters to obtain a dynamic pre-estimated torque value M corresponding to the real-time operation parameters 3 A second displacement coefficient k 2 And a second temperature coefficient M 4 ；
Calculating the steady-state torque compensation value M according to a second formula D The second formula is M D ＝M 3 *k 2 +M 4 。
Optionally, determining a real-time torque compensation value according to the steady-state torque compensation value, the dynamic torque compensation value and the torque filtering time includes:
the real-time torque compensation value at the start of the compressor is equal to M 1 +M 2 ；
The real-time torque compensation value is equal to M within the torque filtering time of the compressor starting 1 +k 3 *M 2 Wherein the attenuation coefficient k 3 Greater than 0 and less than 1, attenuation coefficient k 3 Is inversely related to the increase in time;
after the torque filtering time, the real-time torque compensation value is equal to M 1 。
Optionally, obtaining a steady state predicted torque value M corresponding to the real-time operating parameter 1 First coefficient of displacement k 1 And a first temperature coefficient M 2 The method comprises the following steps:
obtaining a steady-state estimated torque value M corresponding to the real-time operation parameter from the steady-state operation parameter table by using an interpolation method 1 First coefficient of displacement k 1 And a first temperature coefficient M 2 ；
Inquiring the dynamic operation parameter table according to the real-time operation parameters to obtain a dynamic pre-estimated torque value M corresponding to the real-time operation parameters 3 A second displacement coefficient k 2 And a second temperature coefficient M 4 The method comprises the following steps:
obtaining a dynamic pre-estimated torque value M corresponding to the real-time operation parameter from the dynamic operation parameter table by using an interpolation method 3 A second displacement coefficient k 2 And a second temperature coefficient M 4 。
In a second aspect, an embodiment of the present invention further provides a control device for torque compensation of an automotive variable displacement compressor, the control device for torque compensation of an automotive variable displacement compressor includes an experimental data acquisition module, a parameter acquisition module, a table look-up module, a calculation module and an adjustment module, the experimental data acquisition module is configured to acquire a steady-state operation parameter table, a dynamic operation parameter table and a filtering time table according to an automotive engine bench and an automotive test, where the steady-state operation parameter table can show a relationship between a steady-state torque compensation value and an operation parameter under a steady-state operation condition, the dynamic operation parameter table can show a relationship between a dynamic torque compensation value generated at an instant of compressor actuation and the operation parameter, and the filtering time table can show a relationship between filtering time and the operation parameter; the parameter acquisition module is used for acquiring real-time running parameters of the automobile; the table look-up module is used for inquiring the steady-state operation parameter table according to the real-time operation parameters so as to determine the steady-state torque compensation value; inquiring the dynamic operation parameter table according to the real-time operation parameters to determine the dynamic torque compensation value; querying the filtering schedule according to the real-time operating parameters to determine a torque filtering time; the calculation module is used for determining a real-time torque compensation value according to the steady-state torque compensation value, the dynamic torque compensation value and the torque filtering time; the adjusting module is used for adjusting the output power of the engine according to the real-time torque compensation value.
In a third aspect, an embodiment of the present invention further provides a control system for torque compensation of an automotive variable displacement compressor, where the control system for torque compensation of an automotive variable displacement compressor includes an air conditioner control device, an engine, a compressor pressure sensing device, an intake air temperature sensing device, a displacement regulating solenoid valve, and the control device for torque compensation of an automotive variable displacement compressor according to the second aspect.
The method, the device and the system for controlling the torque compensation of the variable displacement compressor of the automobile provided by the embodiment of the invention adopt a mode of an automobile engine rack and an entire automobile test to obtain a steady-state operation parameter table, a dynamic operation parameter table and a filtering time table, acquire real-time operation parameters when the torque compensation value of the compressor needs to be determined, determine the steady-state torque compensation value corresponding to the real-time operation parameters according to the steady-state operation parameter table, determine the dynamic torque compensation value corresponding to the real-time operation parameters according to the dynamic operation parameter table, determine the filtering time corresponding to the real-time operation parameters according to the filtering time table, further determine the real-time torque compensation value of each stage according to the steady-state torque compensation value, the dynamic torque compensation value and the filtering time, realize the determination of the torque compensation of the compressor under the condition of different displacement of the automobile, divide the torque compensation value into a dynamic part and a steady-state part to be determined respectively, and then, a real-time torque compensation value is determined according to the stage of the compressor, so that the real-time torque compensation value is not only associated with the real-time operation parameter, but also adjusted according to the stage of the compressor, and the control accuracy of the torque compensation of the compressor is improved.
Drawings
FIG. 1 is a schematic flow chart illustrating a method for controlling torque compensation of a variable displacement compressor of an automobile according to an embodiment of the present invention;
FIG. 2 is a schematic diagram of a real-time torque compensation value of a compressor over time according to an embodiment of the present invention;
FIG. 3 is a schematic flow chart illustrating another control method for torque compensation of a variable displacement compressor of an automobile according to an embodiment of the present invention;
FIG. 4 is a schematic diagram of three real-time torque compensation values versus time provided by an embodiment of the present invention;
FIG. 5 is a schematic structural diagram of a control device for torque compensation of a variable displacement compressor of an automobile according to an embodiment of the present invention;
fig. 6 is a schematic structural diagram of a control system for torque compensation of an automotive variable displacement compressor according to an embodiment of the present invention.
Detailed Description
In order to make the technical solutions of the present invention better understood, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
It should be noted that the terms "first," "second," and the like in the description and claims of the present invention and in the drawings described above are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used is interchangeable under appropriate circumstances such that the embodiments of the invention described herein are capable of operation in sequences other than those illustrated or described herein. Moreover, the terms "comprises," "comprising," and "having," and any variations thereof, are intended to cover a non-exclusive inclusion, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements expressly listed, but may include other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.
In order to solve the problems in the background art, the embodiment of the invention provides a control method for torque compensation of a variable displacement compressor of an automobile, and the control method is suitable for determining a torque compensation value of the compressor according to an operation parameter of the automobile. The control method for the torque compensation of the automobile variable displacement compressor can be implemented by adopting a control device for the torque compensation of the automobile variable displacement compressor, and the device can be integrated in a vehicle control unit of an automobile. Fig. 1 is a schematic flow chart of a control method for torque compensation of a variable displacement compressor of an automobile according to an embodiment of the present invention, and referring to fig. 1, the control method for torque compensation of a variable displacement compressor of an automobile includes:
s101, acquiring a steady-state operation parameter table, a dynamic operation parameter table and a filtering time table according to an automobile engine pedestal and an entire automobile test.
Fig. 2 is a schematic diagram of a real-time torque compensation value of a compressor varying with time according to an embodiment of the present invention. Referring to fig. 2, the automobile engine bench test refers to an operation of performing test operation on the automobile engine bench according to preset operation parameters. The whole vehicle test refers to a vehicle cooperative operation test performed by the vehicle according to preset operation parameters. The steady state operation parameter table can show the relationship between the steady state torque compensation value of the compressor and the operation parameter under the steady state operation state. The dynamic operation parameter table can show a relation between a dynamic torque compensation value of the compressor and an operation parameter in a dynamic operation state. The filtering schedule can show the relation of the filtering time to the operation parameter. The steady state operation refers to a state in which the compressor is continuously operated with outputting a stable torque. The dynamic operation refers to a transient operation state in which the torque of the compressor is changed due to suction or load change. Steady state torque compensation value M w Refers to the amount of torque provided by the compressor during steady state operation of the engine. Dynamic torque compensation value M D Means that the compressor provides an exceeding steady-state torque compensation value M under the condition that the engine is in a dynamic operation state w Partial additional torque values. The operation parameters refer to various state parameters of the compressor and the engine in the running process of the automobile, and can comprise one or more of parameters such as the rotating speed of the engine, the pressure value of the compressor, the discharge capacity of the compressor, the inlet air temperature of the compressor and the like. Filter elementWave time t 0 The method refers to a time period from the end of a dynamic operation stage after the suction of a compressor to the beginning of the steady state operation of the compressor, and in the time period, the real-time torque compensation of the compressor is attenuated and tends to a steady state torque compensation value M W 。
Specifically, an automobile engine rack and an entire automobile test are carried out on an automobile, the automobile is operated under preset operation parameters, the torque compensation value of the compressor is measured, so that the relative relation between each operation parameter and the torque compensation value of the compressor is obtained, and a steady-state operation parameter table, a dynamic operation parameter table and a filtering time table are formed. The setting of the operation parameters can be realized by adjusting the control parameters of the vehicle-mounted control system and changing the experimental environment through experimental equipment
Exemplary operating parameters include engine speed, compressor pressure value, compressor displacement, and compressor inlet air temperature. The automobile engine bench and the whole automobile test process can comprise a dynamic whole automobile test and a steady-state bench test. In a steady state bench test, one or both of the operating parameters may be adjusted in sequence while the other operating parameters are held constant. Measuring steady-state torque compensation value M after engine stable operation w Thereby obtaining a steady-state torque compensation value M w And the relationship with the one or two operating parameters forms a steady state operating parameter table.
Similar to the steady-state bench test, in the dynamic whole vehicle test, other operation parameters can be kept unchanged, and one or two operation parameters can be adjusted in sequence. Measuring dynamic torque compensation value M at the moment of starting the compressor (within a preset time period after starting the compressor, the preset time period can be less than 2 seconds) D Thereby obtaining a dynamic torque compensation value M D And the relation with the one or two operation parameters forms a dynamic operation parameter table. In the dynamic test process, the filtering time from the start of the compressor to the stable operation of the engine (the torque compensation value of the compressor reaches a steady state value) can be measured, so that the filtering time t can be obtained 0 And forming a dynamic operation parameter table according to the relation between the operation parameters and the operation parameters.
S102, acquiring real-time running parameters of the automobile.
The real-time operation parameters refer to various state parameters of a compressor and an engine in the current operation process of the automobile, correspond to the operation parameters of the automobile engine pedestal and the whole automobile test process, and can comprise one or more of parameters such as real-time engine rotating speed, real-time compressor pressure value, real-time compressor discharge capacity and real-time compressor inlet air temperature.
Specifically, real-time running parameters of the automobile are obtained in response to an air conditioner starting signal input by a user. The real-time operating parameter of the vehicle may be obtained by measuring the real-time operating parameter of the vehicle using various sensors, for example, a pressure sensor to measure a real-time compressor pressure value. The real-time operation parameters of the automobile can also be obtained by determining the real-time operation parameters of the automobile according to operation state signals of various actuators, for example, the real-time compressor displacement is determined according to current signals flowing through a displacement regulating solenoid valve.
And S103, inquiring a steady-state operation parameter table according to the real-time operation parameters to determine a steady-state torque compensation value.
Specifically, a steady-state operation parameter table is queried according to the real-time operation parameters, and a steady-state torque compensation value corresponding to the real-time operation parameters is determined. The steady-state torque calculation coefficients corresponding to the real-time operation parameters can be determined from the steady-state operation parameter table, and then the steady-state torque calculation coefficients corresponding to the real-time operation parameters are substituted into a formula to calculate the steady-state torque compensation value according to the relative relationship between the real-time operation parameters and the steady-state torque compensation value. The steady state torque compensation value corresponding to the set of real time operating parameters may also be determined directly from a multi-dimensional steady state operating parameter table. For example, a steady-state pressure calculation coefficient corresponding to a real-time compressor pressure value, a steady-state displacement calculation coefficient corresponding to a real-time compressor displacement and a steady-state temperature calculation coefficient corresponding to a real-time compressor intake temperature in a real-time engine rotating speed state can be determined from a steady-state operation parameter table, and then the steady-state pressure calculation coefficient, the steady-state displacement calculation coefficient and the steady-state temperature calculation coefficient are substituted into a steady-state torque compensation value calculation formula to calculate a steady-state torque compensation value corresponding to a real-time operation parameter.
And S104, inquiring a dynamic operation parameter table according to the real-time operation parameters to determine a dynamic torque compensation value.
Specifically, a dynamic operation parameter table is queried according to the real-time operation parameters, and a dynamic torque compensation value corresponding to the real-time operation parameters is determined. Similar to the determination of the steady-state torque compensation value, in the process of determining the dynamic torque compensation value, the dynamic torque calculation coefficients corresponding to the real-time operation parameters may be determined from the dynamic operation parameter table, and then the dynamic torque calculation coefficients corresponding to the real-time operation parameters are substituted into a formula to calculate the dynamic torque compensation value according to the relative relationship between the real-time operation parameters and the dynamic torque compensation value. The dynamic torque compensation value corresponding to the set of real-time operating parameters may also be determined directly from a multi-dimensional dynamic operating parameter table. For example, a dynamic pressure calculation coefficient corresponding to a real-time compressor pressure value, a dynamic displacement calculation coefficient corresponding to a real-time compressor displacement, and a dynamic temperature calculation coefficient corresponding to a real-time compressor intake temperature in a real-time engine rotation speed state may be determined from the dynamic operation parameter table, and then the dynamic pressure calculation coefficient, the dynamic displacement calculation coefficient, and the dynamic temperature calculation coefficient may be substituted into the dynamic torque compensation value calculation formula to calculate a dynamic torque compensation value corresponding to the real-time operation parameter.
And S105, inquiring a filtering time table according to the real-time operation parameters to determine the torque filtering time.
Specifically, in the process of determining the torque filtering time, the torque filtering time corresponding to the real-time operation parameter may be determined according to a filtering schedule, where the real-time operation parameter used for determining the torque filtering time may be one or more operation parameters with the highest correlation with the torque filtering time in the multiple real-time operation parameters. Illustratively, the torque filter time corresponding to the real-time compressor pressure value is looked up from a filter schedule.
And S106, determining a real-time torque compensation value according to the steady-state torque compensation value, the dynamic torque compensation value and the torque filtering time.
Specifically, with continued reference to fig. 2, the torque compensation value of the compressor is divided into three stages, the first stage is a torque impact time stage after the compressor is closedA stage in which the compressor is in a dynamic operation state. In the stage, a large impact torque compensation value is introduced due to the suction of the compressor, and the real-time torque compensation value reaches a peak value, namely a dynamic torque compensation value M D Plus steady state torque compensation value M W . The duration of the first phase may be determined experimentally or set empirically, and may be 0.5s, for example. The second stage is the period from the suction impact of the compressor to the stable running state of the compressor, the second stage is the attenuation stage of the torque of the compressor, and the duration is equal to the filtering time t 0 During the period, the operation state of the compressor tends to be stable, and the torque compensation value of the compressor is also from the torque peak value (namely, the dynamic torque compensation value M) D + steady state torque compensation value M W ) Decaying over time to a steady state torque compensation value M W . In the second stage, the real-time torque compensation value is the dynamic torque compensation value M D And a time coefficient k T The product of (d) plus the steady state torque compensation value M W Wherein the time coefficient k T Is a time-dependent negative correlation coefficient which decreases over time such that the torque compensation value is represented by M in real time during the filter time D +M W Attenuation to M W The specific time coefficient setting can be selected and set according to the user requirements and the experimental effect. The third stage is the time stage after the compressor enters the stable operation state, in the time stage, the compressor stably operates and the load is not changed, and the real-time torque compensation value is also stable and not changed and is equal to the steady-state torque compensation value M W 。
And S107, adjusting the output torque of the engine according to the real-time torque compensation value.
Specifically, the output torque of the engine is correspondingly adjusted according to the real-time torque compensation value of the compressor, for example, the fuel injection amount of the engine can be adjusted according to the real-time torque compensation value of the compressor to adjust the output torque of the engine, so that the output torque of the engine can be correspondingly adjusted along with the torque compensation value required by the compressor, and engine vibration and noise caused by uneven supply and demand are avoided.
The control method for the torque compensation of the variable displacement compressor of the automobile provided by the embodiment of the invention adopts a mode of an automobile engine rack and an entire automobile test to obtain a steady-state operation parameter table, a dynamic operation parameter table and a filtering time table, acquires real-time operation parameters when the torque compensation value of the compressor needs to be determined, determines the steady-state torque compensation value corresponding to the real-time operation parameters according to the steady-state operation parameter table, determines the dynamic torque compensation value corresponding to the real-time operation parameters according to the dynamic operation parameter table, determines the filtering time corresponding to the real-time operation parameters according to the filtering time table, further determines the real-time torque compensation value of each stage according to the steady-state torque compensation value, the dynamic torque compensation value and the filtering time, realizes the determination of the torque compensation of the compressor under the condition of different displacement of the automobile, divides the torque compensation value into a dynamic part and a steady-state part to respectively look up tables for determination, and then the real-time torque compensation value is determined according to the stage of the compressor, so that the real-time torque compensation value is not only associated with the real-time operation parameters, but also adjusted according to the stage of the compressor, the control accuracy of the torque compensation of the compressor is improved, the noise and the vibration of the engine are reduced, and the driving comfort is improved.
Fig. 3 is a schematic flow chart of another control method for torque compensation of a variable displacement compressor of an automobile according to an embodiment of the present invention, and referring to fig. 3, the control method for torque compensation of a variable displacement compressor of an automobile includes:
s201, acquiring the relation between a steady-state torque compensation value and a compressor pressure value under each engine rotating speed condition according to an automobile engine pedestal and an entire automobile test, and generating a first steady-state table.
The first steady state table comprises engine speed, compressor pressure values and a steady state predicted torque value M1 under the condition of corresponding engine speed and corresponding compressor pressure values. The steady state predicted torque value M1 is the predicted torque value in the equation for calculating the steady state torque compensation value, and is related to the compressor pressure value.
Specifically, the calculation formula of the steady-state torque compensation of the compressor is a first formula M W ＝M 1 *k 1 +M 2 Wherein M is 1 For steady state predicted torque values, related to compressor pressure values, k 1 Is a first displacement factor, related to compressor displacement. M 2 Is a first temperature coefficient associated with an engine intake air temperature value. In the test of an automobile engine bench and the whole automobile, the displacement of the compressor is kept to be the maximum displacement value, the air inlet temperature of the compressor is kept unchanged, and the pressure value of the compressor is sequentially adjusted under the condition that the rotating speed of the engine is set to be a first preset value. And measuring a steady-state torque compensation value of the compressor after the compressor stably runs after the pressure value of one compressor is set. And adjusting the rotating speed of the engine and repeating the tests until the pressure values of all the compressors are tested under the condition that the rotating speed of the engine is the first preset value. Determining a steady-state estimated torque value M according to the measured steady-state torque compensation value 1 And generating a first steady state table. For example, a steady state torque compensation value measured corresponding to each engine speed and compressor pressure condition may be determined as the steady state predicted torque value M1. The first steady state table provided by the embodiment of the present invention is shown in table 1:
Figure BDA0003692647750000131
Figure BDA0003692647750000141
TABLE 1 first Steady State Table
The contents of the first column in table 1 are compressor pressure values in MPa; the first row contains engine speed in rpm. In the table, the steady state estimated torque value M is determined under the conditions of each compressor pressure value and each engine speed 1 In the table, only schematic representation is given.
S202, acquiring the relation between the steady-state torque compensation value and the compressor displacement under each engine rotating speed condition according to an automobile engine pedestal and an entire automobile test, and generating a second steady-state table.
Wherein the second steady state table includes engine speed, compressor displacement, and, for a corresponding engine speed and a corresponding compressor displacement, a first displacement coefficient k 1 。
In particular toSteady state predicted torque M 1 Measured for maximum displacement, the compressor of the invention is a variable displacement compressor, and the steady state estimated torque M 1 The influence of the compressor pressure value on the steady-state torque compensation value can only be shown, but the influence of the compressor displacement on the steady-state torque compensation value cannot be shown, so that a first displacement coefficient k related to the compressor displacement needs to be introduced 1 . In the test of an automobile engine bench and the whole automobile, the pressure value of a compressor and the inlet air temperature of the compressor are kept unchanged, and the current of an electromagnetic valve is sequentially adjusted under the condition that the rotating speed of an engine is set to be a first preset value, wherein the electromagnetic valve is a displacement adjusting electromagnetic valve of the compressor, and the current of the electromagnetic valve corresponds to the displacement of the compressor. And measuring the steady-state torque compensation value of the compressor after the current value of each electromagnetic valve is set and the compressor stably runs. And (4) until the test of the current values of all the electromagnetic valves is completed under the condition that the rotating speed of the engine is the first preset value, adjusting the rotating speed of the engine and repeating the test. Determining a first displacement coefficient k according to the measured steady-state torque compensation value 1 And generating a second steady state table. In addition, if the relationship between the steady-state torque compensation value of the compressor and the displacement of the compressor is different under the condition of finding different pressure values of the compressor, the pressure value of the compressor can be adjusted and the experiment can be repeated to obtain a plurality of second steady-state tables. A second steady state table provided in the embodiment of the present invention is shown in table 2:
Figure BDA0003692647750000151
TABLE 2 second Steady State Table
The contents of the first column in table 2 are solenoid valve currents in units of a; the first row content is engine speed, rpm. The table indicates the first displacement factor K1 determined for each compressor displacement and each engine speed.
S203, obtaining the relation between the steady-state torque compensation value and the air inlet temperature of the compressor under the condition of each engine rotating speed according to the automobile engine pedestal and the whole automobile test, and generating a third steady-state table.
Wherein the third steady state table comprises engine speed and pressureA compressor inlet air temperature, and a first temperature coefficient M at a corresponding engine speed and a corresponding compressor inlet air temperature 2 。
Specifically, the working torque of the variable displacement compressor is also influenced by the inlet air temperature, so in order to improve the calculation accuracy of the steady-state torque compensation value, a first temperature coefficient M related to the inlet air temperature of the compressor can be further added 2 . In the test of an automobile engine bench and the whole automobile, the pressure value and the displacement of a compressor are kept unchanged, and the ambient temperature of an experimental site is sequentially adjusted to change the air inlet temperature of the compressor under the condition that the rotating speed of an engine is set to be a first preset value. And measuring a steady-state torque compensation value of the compressor after the compressor stably runs and when the inlet air temperature of one compressor is set. And (4) until the test of the inlet air temperature of all the compressors is completed under the condition that the rotating speed of the engine is the first preset value, adjusting the rotating speed of the engine and repeating the test. Determining a first temperature coefficient M according to the measured steady-state torque compensation value 2 And generating a third steady state table. In addition, if the relationship between the steady-state torque compensation value of the compressor and the inlet air temperature of the compressor is different under the condition of finding different pressure values of the compressor, the pressure value of the compressor can be adjusted and the experiment can be repeated to obtain a plurality of third steady-state tables. A third steady state table provided in the embodiment of the present invention is shown in table 3:
Figure BDA0003692647750000161
TABLE 3 third Steady State Table
The contents of the first column in table 3 are compressor inlet temperatures in units; the first row content is engine speed, rpm. The first temperature coefficient M2 determined for each compressor inlet air temperature and each engine speed condition is shown only schematically.
S204, acquiring the relation between the dynamic torque compensation value and the compressor pressure value under the condition of each engine rotating speed according to an automobile engine pedestal and an entire automobile test, and generating a first dynamic table.
Wherein the first dynamic table comprises the rotating speed of the engine and the pressure value of the compressor,and dynamically estimating the torque peak value M under the condition of corresponding engine speed and corresponding compressor pressure value 3 。
Specifically, at the moment after the compressor is closed, an extra load is generated on the engine, and at this moment, the dynamic torque compensation value M needs to be calculated D To adjust the output torque of the engine. Dynamic torque compensation value M D Is M D ＝M 3 *k 2 +M 4 Wherein M is 3 For dynamically estimating the torque value, k, being related to the compressor pressure value 3 And is the second displacement coefficient, related to the compressor displacement. M 4 Is a second temperature coefficient, is associated with the engine intake air temperature value. In the test of an automobile engine bench and the whole automobile, the displacement of the compressor is kept to be the maximum displacement value, the air inlet temperature of the compressor is kept unchanged, and the pressure value of the compressor is sequentially adjusted under the condition that the rotating speed of the engine is set to be a first preset value. When the pressure value of one compressor is set, the instantaneous dynamic torque compensation value after the compressor is started is measured, namely the peak value of extra impact torque generated instantaneously due to the suction of the compressor. And (4) until the test of all the compressor pressure values is completed under the condition that the rotating speed of the engine is the first preset value, adjusting the rotating speed of the engine, and repeating the test. Determining a dynamic pre-estimated torque value M according to the measured dynamic torque compensation value 3 And generating a first dynamic table. For example, a dynamic torque compensation value measured corresponding to each engine speed and compressor pressure value may be determined as the dynamic predicted torque value M 3 . The first dynamic table is similar to the first static table in the setting format, and dynamic predicted torque values M determined under the conditions of various compressor pressure values and various engine rotating speeds are set in the table 3 And will not be described in detail herein.
S205, obtaining the relation between the filtering time and the pressure value of the compressor according to the automobile engine pedestal and the whole automobile test, and generating a filtering time table.
Specifically, in the automobile engine bench and the whole automobile test, the compressor displacement is kept as the maximum displacement value, the air inlet temperature of the compressor and the engine speed are unchanged, and the pressure value of the compressor is sequentially adjusted. When the pressure value of one compressor is set, the compressor is measured after the compressor is startedIs attenuated to a duration filtering time t of the steady-state torque compensation value by the sum of the dynamic torque compensation value and the steady-state torque compensation value 0 . And forming a filtering time table until all the compressor pressure values are tested. The filtering schedule provided by the embodiment of the invention is shown in table 4:
pressure value 6000 8000 10000 12000 16000 20000 24000 26000 28000
Time of filtering * * * * * * * * *
TABLE 4 Filtering schedules
The contents of the first row in table 1 are compressor pressure values in MPa; the second line content being the filtering time t 0 The unit is s. In the table, the filter time t determined for each compressor pressure value 0 In the table, only schematic representation is given.
S206, acquiring the relation between the dynamic torque compensation value and the compressor displacement under the condition of each engine rotating speed according to the automobile engine pedestal and the whole automobile test, and generating a second dynamic table.
Wherein the second dynamic table includes engine speed, compressor displacement, and, for a corresponding engine speed and a corresponding compressor displacement, a second displacement factor k 2 。
Specifically, dynamic predicted torque M is obtained similar to the steady state operating parameter table acquisition process 3 Also measured at maximum displacement, and the compressor to which the invention relates is a variable displacement compressor, the torque M being dynamically estimated 3 Only the influence of the compressor pressure value on the dynamic torque compensation value can be shown, but not the influence of the compressor displacement on the dynamic torque compensation value, so that a second displacement coefficient k related to the compressor displacement needs to be introduced 2 . In the test of an automobile engine bench and the whole automobile, the pressure value of a compressor and the inlet air temperature of the compressor are kept unchanged, and the current of an electromagnetic valve is sequentially adjusted under the condition that the rotating speed of an engine is set to be a first preset value, wherein the electromagnetic valve is a displacement adjusting electromagnetic valve of the compressor, and the current of the electromagnetic valve corresponds to the displacement of the compressor. And measuring the dynamic torque compensation value of the compressor at the suction moment of the compressor every time the current value of the electromagnetic valve is set. And (4) until the test of the current values of all the electromagnetic valves is completed under the condition that the rotating speed of the engine is the first preset value, adjusting the rotating speed of the engine, and repeating the test. Determining a second displacement coefficient k according to the measured dynamic state torque compensation value 2 And generating a second dynamic table. In addition, if the pressure value of the compressor is found to be different, the dynamic torque of the compressorThe relationship between the compensation value and the compressor displacement is different, and the compressor pressure value can be adjusted and the experiment can be repeated to obtain a plurality of second dynamic tables. The second dynamic table is similar to the second static table in layout format, wherein the dynamic predicted torque value k is determined for each compressor displacement value and each engine speed condition 2 And will not be described herein.
And S207, acquiring the relation between the dynamic torque compensation value and the air inlet temperature of the compressor under the condition of each engine rotating speed according to the automobile engine stand and the whole automobile test, and generating a third dynamic table.
Wherein the third dynamic table includes engine speed, compressor inlet air temperature, and, for a corresponding engine speed and a corresponding compressor inlet air temperature, a second temperature coefficient M 4 。
Specifically, the working torque of the variable displacement compressor also receives the influence of the inlet air temperature, so in order to improve the calculation precision of the dynamic torque compensation value, a second temperature coefficient M related to the inlet air temperature of the compressor can be further added 4 . In the test of an automobile engine bench and the whole automobile, the pressure value and the displacement of a compressor are kept unchanged, and the ambient temperature of an experimental site is sequentially adjusted to change the air inlet temperature of the compressor under the condition that the rotating speed of an engine is set to be a first preset value. And measuring the dynamic torque compensation value of the compressor at the suction moment of the compressor every time the air inlet temperature of the compressor is set. And (4) until the test of the inlet air temperature of all the compressors is completed under the condition that the rotating speed of the engine is the first preset value, adjusting the rotating speed of the engine and repeating the test. Determining a second temperature coefficient M according to the measured dynamic torque compensation value 4 And generating a third dynamic table. In addition, if the relationship between the dynamic torque compensation value of the compressor and the inlet air temperature of the compressor is different under the condition of finding different compressor pressure values, the compressor pressure value can be adjusted and the experiment can be repeated to obtain a plurality of third dynamic tables. The third dynamic table is similar to the third static table in layout format, and the second temperature coefficient M determined under the conditions of each compressor inlet air temperature and each engine rotating speed is represented in the table 4 And will not be described herein.
And S208, acquiring real-time running parameters of the automobile.
Step S208 is the same as step S102, and is not described herein again.
S209, inquiring the steady-state operation parameter table according to the real-time operation parameters to obtain a steady-state estimated torque value M corresponding to the real-time operation parameters 1 First coefficient of displacement k 1 And a first temperature coefficient M 2 。
Specifically, a first steady state table is checked according to the real-time engine rotating speed and the real-time compressor pressure value to determine a corresponding steady state estimated torque value M 1 . Checking a second steady state table according to the real-time engine rotating speed and the real-time electromagnetic valve current to determine a corresponding first displacement coefficient k 1 . Checking a third steady state table according to the real-time engine rotating speed and the real-time compressor inlet air temperature to determine a corresponding first temperature coefficient M 2 . It should be noted that, in the table look-up process, if the operation parameter in the table is not equal to the real-time operation parameter, an interpolation method may be used to determine the value corresponding to the real-time operation parameter.
S210, calculating a steady-state torque compensation value M according to a first formula W The first formula is M W ＝M 1 *k 1 +M 2 。
Specifically, the steady state predicted torque value M1 and the first displacement coefficient k corresponding to the real-time operation parameters 1 And a first temperature coefficient M 2 Substituting into a first formula M W ＝M 1 *k 1 +M 2 Calculating to obtain a steady-state torque compensation value M W 。
S211, inquiring the dynamic operation parameter table according to the real-time operation parameters to obtain a dynamic pre-estimated torque value M corresponding to the real-time operation parameters 3 A second displacement coefficient k 2 And a second temperature coefficient M 4 。
Specifically, while step S208 is being performed, the first dynamic table is looked up according to the real-time engine speed and the real-time compressor pressure value to determine the corresponding dynamic predicted torque value M 3 . Checking a second dynamic table according to the real-time engine rotating speed and the real-time electromagnetic valve current to determine a corresponding second displacement coefficient k 2 . Checking the third dynamic table according to the real-time engine speed and the real-time compressor inlet air temperature to determine the correspondingFirst temperature coefficient M 2 。
S212, calculating a steady-state torque compensation value M according to a second formula D The second formula is M D ＝M 3 *k 2 +M 4 。
Specifically, a dynamic predicted torque value M corresponding to the real-time operating parameters 3 A second displacement coefficient k 2 And a second temperature coefficient M 4 Substituting into a first formula M D ＝M 3 *k 2 +M 4 Calculating to obtain dynamic torque compensation value M D 。
S213, determining the filtering time t from the filtering time table according to the real-time operation parameters 0 。
Specifically, a filtering time table is inquired according to the real-time compressor pressure value in the real-time operation parameters, and filtering time t corresponding to the real-time compressor pressure value is determined 0 。
And S214, determining a real-time torque compensation value according to the steady-state torque compensation value, the dynamic torque compensation value and the torque filtering time.
Specifically, the compressor may generate an additional impact torque peak due to the moment after the compressor is pulled in. Therefore, the real-time torque compensation value is equal to M within the first preset time after the compressor is started 1 +M 2 The torque of the compressor is at a higher level during this process. After a first preset time after the compressor is started, the filtering time t continues 0 Real-time torque compensation value equal to M 1 +k 3 *M 2 Wherein the attenuation coefficient k 3 Greater than 0 and less than 1, the attenuation of the compressor torque during this attenuation time can be achieved by means of filtering, the attenuation factor k 3 The time is inversely related to the increase of the time, so that the impact on the engine generated in the moment of suction of the compressor can be relieved, the engine can be better transited to a steady-state running state, the engine can be protected, and the comfort can be improved. After the torque filtering time, the real-time torque compensation value equals the steady-state torque compensation value M 1 . It is to be noted that the attenuation coefficient k 3 For the coefficients with respect to time t, t may be defined as t 1 In the case of (2) making the real-time torque compensation value equal to M 1 +M 2 To is thatAt t ═ t 1 +t 0 In the case of (3) making the real-time torque compensation value equal to M 1 And t is at t 1 To t ═ t 1 +t 0 In the process, the real-time torque compensation value is uniformly attenuated, and the specific attenuation coefficient value can be determined according to experiments. Exemplarily, fig. 4 is a schematic diagram of a relationship between three real-time torque compensation values and time provided by an embodiment of the invention, and referring to fig. 4, it can be known that the attenuation coefficient k 3 The real-time torque compensation value can be made at the filtering time t as shown by the curve A 0 The inner straight line is attenuated, and the real-time torque compensation value can be made to be at the filtering time t as shown by a curve B 0 The concave curve attenuates, and the real-time torque compensation value can be further enabled to be at the filtering time t as shown by the curve C 0 The inward convex curve decays.
And S215, adjusting the output torque of the engine according to the real-time torque compensation value.
Step S215 is the same as step S107, and is not described here again.
According to the control method for the torque compensation of the automobile variable displacement compressor, the torque compensation value is divided into a dynamic part and a steady part to be determined by respectively looking up a table, so that the fluctuation of the rotating speed of an engine is small when the compressor is sucked. The air inlet temperature and the displacement of the compressor are considered when the steady-state torque compensation value and the dynamic torque compensation value are determined, and the torque compensation deviation of the compressor caused by the ambient temperature and the torque compensation deviation of the compressor caused by different displacements of the compressor can be accurately adjusted. And then the real-time torque compensation value is determined according to the stage of the compressor, the attenuation in the filtering time is considered, the impact on the engine at the moment of the suction of the compressor is relieved, the stable running state is well transited, the engine can be protected, and the comfort can be improved.
The embodiment of the invention also provides a control device for the torque compensation of the automobile variable displacement compressor. Fig. 5 is a schematic structural diagram of a control device for torque compensation of a variable displacement compressor of an automobile according to an embodiment of the present invention, and referring to fig. 5, the control device 500 for torque compensation of a variable displacement compressor of an automobile includes: the system comprises an experimental data acquisition module 501, a parameter acquisition module 502, a table look-up module 503, a calculation module 504 and an adjustment module, wherein the experimental data acquisition module 501 is used for acquiring a steady-state operation parameter table, a dynamic operation parameter table and a filtering time table according to an automobile engine pedestal and an integral automobile test, wherein the steady-state operation parameter table can show the relation between a steady-state torque compensation value and an operation parameter under the condition of steady-state operation, the dynamic operation parameter table can show the relation between a dynamic torque compensation value and an operation parameter generated at the moment of suction of a compressor, and the filtering time table can show the relation between filtering time and the operation parameter; the parameter acquisition module 502 is used for acquiring real-time running parameters of the automobile; the table look-up module 503 is configured to query a steady-state operation parameter table according to the real-time operation parameter to determine a steady-state torque compensation value; inquiring a dynamic operation parameter table according to the real-time operation parameters to determine a dynamic torque compensation value; querying a filtering schedule according to the real-time operating parameters to determine a torque filtering time; the calculation module 504 is configured to determine a real-time torque compensation value according to the steady-state torque compensation value, the dynamic torque compensation value, and the torque filtering time; the adjustment module 505 is configured to adjust an output power of the engine based on the real-time torque compensation value.
The embodiment of the invention also provides a control system for the torque compensation of the variable displacement compressor of the automobile. Fig. 6 is a schematic structural diagram of a control system for torque compensation of an automotive variable displacement compressor according to an embodiment of the present invention, and referring to fig. 6, the control system 600 for torque compensation of an automotive variable displacement compressor includes an air conditioner control device 601, an engine 602, a compressor 603, a compressor pressure sensing device 604, an intake air temperature sensing device 605, a displacement regulating solenoid valve 606, and a control device 500 for torque compensation of an automotive variable displacement compressor, where the control device for torque compensation of an automotive variable displacement compressor may execute any of the foregoing control methods for torque compensation of an automotive variable displacement compressor.
The method, the device and the system for controlling the torque compensation of the variable displacement compressor of the automobile provided by the embodiment of the invention adopt a mode of an automobile engine rack and an entire automobile test to obtain a steady-state operation parameter table, a dynamic operation parameter table and a filtering time table, acquire real-time operation parameters when the torque compensation value of the compressor needs to be determined, determine the steady-state torque compensation value corresponding to the real-time operation parameters according to the steady-state operation parameter table, determine the dynamic torque compensation value corresponding to the real-time operation parameters according to the dynamic operation parameter table, determine the filtering time corresponding to the real-time operation parameters according to the filtering time table, further determine the real-time torque compensation value of each stage according to the steady-state torque compensation value, the dynamic torque compensation value and the filtering time, realize the determination of the torque compensation of the compressor under the condition of different displacement of the automobile, divide the torque compensation value into a dynamic part and a steady-state part to be determined respectively, and then, a real-time torque compensation value is determined according to the stage of the compressor, so that the real-time torque compensation value is not only associated with the real-time operation parameters, but also adjusted according to the stage of the compressor, the accuracy of the torque compensation value is improved, and the compensation switching between the transition dynamic state and the steady state can be better in a filtering mode.
It should be understood that various forms of the flows shown above may be used, with steps reordered, added, or deleted. For example, the steps described in the present invention may be executed in parallel, sequentially, or in different orders, and are not limited herein as long as the desired results of the technical solution of the present invention can be achieved.
The above-described embodiments should not be construed as limiting the scope of the invention. It should be understood by those skilled in the art that various modifications, combinations, sub-combinations and substitutions may be made in accordance with design requirements and other factors. Any modification, equivalent replacement, and improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (10)

1. A control method for torque compensation of an automobile variable displacement compressor is characterized by comprising the following steps:
according to an automobile engine pedestal and an entire automobile test, a steady-state operation parameter table, a dynamic operation parameter table and a filtering time table are obtained, wherein the steady-state operation parameter table can show the relation between a steady-state torque compensation value and an operation parameter in a steady-state operation state, the dynamic operation parameter table can show the relation between the dynamic torque compensation value and the operation parameter in the steady-state operation state, and the filtering time table can show the relation between filtering time and the operation parameter;
acquiring real-time running parameters of the automobile;
inquiring the steady-state operation parameter table according to the real-time operation parameters to determine the steady-state torque compensation value;
inquiring the dynamic operation parameter table according to the real-time operation parameters to determine the dynamic torque compensation value;
querying the filtering time table according to the real-time operation parameters to determine torque filtering time;
determining a real-time torque compensation value according to the steady-state torque compensation value, the dynamic torque compensation value and the torque filtering time;
and adjusting the output torque of the engine according to the real-time torque compensation value.
2. The method of claim 1, wherein the operating parameters include engine speed, compressor pressure value, compressor displacement, and compressor inlet air temperature.
3. The control method for torque compensation of a variable displacement compressor of an automobile according to claim 2, wherein the steady state operation parameter tables include a first steady state table, a second steady state table, and a third steady state table;
according to the automobile engine rack and the whole automobile test, obtain steady state operation parameter table, dynamic operation parameter table and filtering time table, include:
according to the automobile engine pedestal and the whole automobile test, acquiring the relation between the steady-state torque compensation value and the compressor pressure value under each engine rotating speed condition, and generating a first steady-state table, wherein the first steady-state table comprises the engine rotating speed, the compressor pressure value and a steady-state estimated torque value M under the condition of corresponding engine rotating speed and corresponding compressor pressure value 1 ；
According to the automobile engine rack and the whole automobile test, the relation between the steady-state torque compensation value and the compressor displacement under the condition of each engine rotating speed is obtained to generate the second torque compensation valueA bi-stable table, wherein the second stable table comprises engine speed, the compressor displacement, and, for a corresponding engine speed and a corresponding compressor displacement, a first displacement factor k 1 ；
According to the automobile engine pedestal and the whole automobile test, acquiring the relation between the steady-state torque compensation value and the compressor air inlet temperature under each engine rotating speed condition, and generating a third steady-state table, wherein the third steady-state table comprises the engine rotating speed, the compressor air inlet temperature and a first temperature coefficient M under the condition of corresponding engine rotating speed and corresponding compressor air inlet temperature 2 。
4. The control method for torque compensation of a variable displacement compressor of an automobile according to claim 3, wherein the dynamic operation parameter tables include a first dynamic table, a second dynamic table, and a third dynamic table;
according to the automobile engine rack and the whole automobile test, obtain steady state operation parameter table, dynamic operation parameter table and filtering time table, include:
according to the automobile engine pedestal and the whole automobile test, the relation between the dynamic torque compensation value and the compressor pressure value under each engine rotating speed condition is obtained, and the first dynamic table is generated, wherein the first dynamic table comprises the engine rotating speed, the compressor pressure value and the dynamic pre-estimated torque peak value M under the condition of corresponding engine rotating speed and corresponding compressor pressure value 3 ；
According to the automobile engine rack and the whole automobile test, the relation between the dynamic torque compensation value and the compressor displacement under the condition of each engine speed is obtained, and the second dynamic table is generated, wherein the second dynamic table comprises the engine speed, the compressor displacement and a second displacement coefficient k under the condition of corresponding to the engine speed and the compressor displacement 2 ；
According to the automobile engine pedestal and the whole automobile test, the relation between the dynamic torque compensation value and the air inlet temperature of the compressor under the condition of each engine rotating speed is obtained, and the third dynamic table is generated, wherein the third dynamic table comprises the engine rotating speed and the compressorAn intake air temperature, and a second temperature coefficient M in the case of a corresponding engine speed and a corresponding compressor intake air temperature 4 。
5. The method as claimed in claim 4, wherein the step of querying the steady state operation parameter table according to the real time operation parameter to determine the steady state torque compensation value comprises:
inquiring the steady state operation parameter table according to the real time operation parameters to obtain a steady state estimated torque value M corresponding to the real time operation parameters 1 First coefficient of displacement k 1 And a first temperature coefficient M 2 ；
Calculating the steady state torque compensation value M according to a first formula W The first formula is M W ＝M 1 *k 1 +M 2 。
6. The method for controlling torque compensation of a variable displacement compressor of an automobile according to claim 5, wherein querying the dynamic operation parameter table according to the real-time operation parameters to determine the dynamic torque compensation value comprises:
inquiring the dynamic operation parameter table according to the real-time operation parameters to obtain a dynamic pre-estimated torque value M corresponding to the real-time operation parameters 3 A second displacement coefficient k 2 And a second temperature coefficient M 4 ；
Calculating the steady-state torque compensation value M according to a second formula D The second formula is M D ＝M 3 *k 2 +M 4 。
7. The method for controlling torque compensation of a variable displacement compressor of an automobile according to claim 6, wherein determining a real-time torque compensation value according to the steady-state torque compensation value, the dynamic torque compensation value and the torque filtering time comprises:
the real-time torque compensation value when the compressor is started is equal to M 1 +M 2 ；
The describedThe real-time torque compensation value is equal to M within the torque filtering time of the starting of the compressor 1 +k 3 *M 2 Wherein the attenuation coefficient k 3 Greater than 0 and less than 1, attenuation coefficient k 3 Is inversely related to the increase in time;
after the torque filtering time, the real-time torque compensation value is equal to M 1 。
8. The control method for torque compensation of automobile variable displacement compressor according to claim 6, wherein a steady state predicted torque value M corresponding to the real-time operation parameter is obtained 1 First displacement coefficient k 1 And a first temperature coefficient M 2 The method comprises the following steps:
obtaining a steady-state estimated torque value M corresponding to the real-time operation parameter from the steady-state operation parameter table by using an interpolation method 1 First coefficient of displacement k 1 And a first temperature coefficient M 2 ；
Inquiring the dynamic operation parameter table according to the real-time operation parameters to obtain a dynamic pre-estimated torque value M corresponding to the real-time operation parameters 3 A second displacement coefficient k 2 And a second temperature coefficient M 4 The method comprises the following steps:
obtaining a dynamic estimated torque value M corresponding to the real-time operation parameter from the dynamic operation parameter table by using an interpolation method 3 A second displacement coefficient k 2 And a second temperature coefficient M 4 。
9. A control device for torque compensation of an automotive variable displacement compressor, comprising:
the system comprises an experiment data acquisition module, a dynamic operation parameter table and a filtering time table, wherein the experiment data acquisition module is used for acquiring a steady state operation parameter table, the dynamic operation parameter table and the filtering time table according to an automobile engine stand and an integral automobile test, the steady state operation parameter table can show the relation between a steady state torque compensation value and an operation parameter under a steady state operation condition, the dynamic operation parameter table can show the relation between a dynamic torque compensation value generated at the moment of suction of a compressor and the operation parameter, and the filtering time table can show the relation between filtering time and the operation parameter;
the parameter acquisition module is used for acquiring real-time running parameters of the automobile;
the table look-up module is used for inquiring the steady-state operation parameter table according to the real-time operation parameters so as to determine the steady-state torque compensation value; inquiring the dynamic operation parameter table according to the real-time operation parameters to determine the dynamic torque compensation value; querying the filtering schedule according to the real-time operating parameters to determine a torque filtering time;
the calculation module is used for determining a real-time torque compensation value according to the steady-state torque compensation value, the dynamic torque compensation value and the torque filtering time;
and the adjusting module is used for adjusting the output power of the engine according to the real-time torque compensation value.
10. A control system for torque compensation of an automotive variable displacement compressor, which is characterized by comprising an air conditioner control device, an engine, a compressor pressure sensing device, an air inlet temperature sensing device, a displacement adjusting electromagnetic valve and the control device for torque compensation of the automotive variable displacement compressor, wherein the control device comprises the control device of the torque compensation of the automotive variable displacement compressor, and the control device is used for controlling the torque compensation of the automotive variable displacement compressor.
CN202210669285.2A 2022-06-14 2022-06-14 Control method, device and system for torque compensation of variable displacement compressor Pending CN114962236A (en)

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CN108691673A (en) * 2017-04-10 2018-10-23 福特环球技术公司 Method and system for improving transient torque response
CN112727745A (en) * 2020-12-28 2021-04-30 广东美芝制冷设备有限公司 Control method and device of compressor, refrigeration equipment and readable storage medium
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Publication number Priority date Publication date Assignee Title
US6305350B1 (en) * 2000-06-20 2001-10-23 General Motors Corporation Engine speed control
DE102010030532A1 (en) * 2010-06-25 2011-12-29 Zf Lenksysteme Gmbh Drive-related skewing effects compensating method for motor vehicle, involves identifying earnings per share by using basic assist torque and compensation torque, which counteracts pulling to side
CN103696954A (en) * 2013-12-17 2014-04-02 重庆长安汽车股份有限公司 External control variable displacement compressor torque compensating method and system
CN106828484A (en) * 2017-02-06 2017-06-13 潍柴动力股份有限公司 A kind of engine accessory power rating moment of torsion acquisition methods and device
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