CN108869839B - Flow compensation method and device of flow variable force electromagnetic valve - Google Patents
Flow compensation method and device of flow variable force electromagnetic valve Download PDFInfo
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- CN108869839B CN108869839B CN201710329889.1A CN201710329889A CN108869839B CN 108869839 B CN108869839 B CN 108869839B CN 201710329889 A CN201710329889 A CN 201710329889A CN 108869839 B CN108869839 B CN 108869839B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0675—Electromagnet aspects, e.g. electric supply therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0003—Arrangement or mounting of elements of the control apparatus, e.g. valve assemblies or snapfittings of valves; Arrangements of the control unit on or in the transmission gearbox
- F16H61/0009—Hydraulic control units for transmission control, e.g. assembly of valve plates or valve units
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
- F16H61/0262—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic
- F16H61/0276—Elements specially adapted for hydraulic control units, e.g. valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
- F16H61/06—Smoothing ratio shift by controlling rate of change of fluid pressure
- F16H61/061—Smoothing ratio shift by controlling rate of change of fluid pressure using electric control means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
- F16H61/0262—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic
- F16H61/0276—Elements specially adapted for hydraulic control units, e.g. valves
- F16H2061/0279—Details of hydraulic valves, e.g. lands, ports, spools or springs
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Electromagnetism (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Control Of Transmission Device (AREA)
Abstract
The invention provides a flow compensation method and a device of a flow variable force electromagnetic valve, wherein the method comprises the following steps: setting a target flow of a flow variable force electromagnetic valve, so that a piston of an oil cavity of a clutch actuator moves under the action of the flow variable force electromagnetic valve; in a preset displacement range, according to the moving state of the piston, the target flow and the sectional area of an oil cavity of the clutch actuator, calculating a flow compensation point corresponding to the target flow, wherein the flow compensation point indicates the relation between the target flow and the actual flow; and carrying out flow compensation on the flow variable force electromagnetic valve according to the flow compensation point. The method and the device can lead the compensated flow to be consistent with the target flow, thereby realizing the accurate control of the clutch.
Description
Technical Field
The invention relates to the field of automobiles, in particular to a flow compensation method and device of a flow variable force electromagnetic valve.
Background
A flow Variable Force Solenoid (Q-VFS) may be used to control the clutch. Generally, the flow control of the flow variable force solenoid valve can be realized by changing a control signal of the flow variable force solenoid valve to obtain a target flow, so that the clutch can be controlled.
However, during application, there is a problem that the actual flow rate does not match the target flow rate, which in turn leads to a problem that the control of the clutch is inaccurate.
Disclosure of Invention
The invention solves the technical problem that the actual flow of the flow variable force electromagnetic valve does not accord with the target flow.
In order to solve the above technical problem, an embodiment of the present invention provides a flow compensation method for a flow variable force solenoid valve, including: setting a target flow of a flow variable force electromagnetic valve, so that a piston of an oil cavity of a clutch actuator moves under the action of the flow variable force electromagnetic valve; in a preset displacement range, according to the moving state of the piston, the target flow and the sectional area of an oil cavity of the clutch actuator, calculating a flow compensation point corresponding to the target flow, wherein the flow compensation point indicates the relation between the target flow and the actual flow; and carrying out flow compensation on the flow variable force electromagnetic valve according to the flow compensation point.
Optionally, the obtaining of the flow compensation point corresponding to the target flow includes: calculating the average value of the actual speed of the piston in the preset displacement range; calculating the product of the actual speed average value and the sectional area of the oil cavity of the clutch actuator as the actual flow; calculating a ratio between the target flow rate and the actual flow rate as the flow compensation point.
Optionally, calculating the actual speed of the piston movement comprises: carrying out average rolling filtering on the actual displacement time curve of the piston in the preset displacement range; calculating the slope of the displacement time curve after the average rolling filtration; low pass filtering the slope to obtain the actual speed average.
Optionally, before performing flow compensation on the flow variable force solenoid valve according to the flow compensation point, the method further includes: and determining that the flow compensation point is within a preset range.
Optionally, the setting of the target flow of the flow variable force solenoid valve includes: and setting different target flow rates within the flow range of the flow variable force electromagnetic valve.
Optionally, before setting the target flow of the flow variable force solenoid valve, the method further includes: and determining that the pressure of a main oil way of the flow variable-force electromagnetic valve exceeds a preset value, and the gear shifting fork corresponding to the oil cylinder of the clutch actuator is located at the middle position.
Optionally, the oil cavity of the clutch actuator is located in a clutch of the double-clutch transmission, in which a corresponding shift fork is located in the middle position.
The embodiment of the present invention further provides a flow compensation device for a flow variable force solenoid valve, including: the target flow setting unit is suitable for setting the target flow of the flow variable force electromagnetic valve, so that a piston of an oil cavity of the clutch actuator moves under the action of the flow variable force electromagnetic valve; the compensation point calculation unit is suitable for calculating a flow compensation point corresponding to the target flow according to the moving state of the piston, the target flow and the sectional area of an oil cavity of the clutch actuator in a preset displacement range, and the flow compensation point indicates the relation between the target flow and the actual flow; and the flow compensation unit is suitable for carrying out flow compensation on the flow variable force electromagnetic valve according to the flow compensation point.
Optionally, the compensation point calculating unit includes: the actual speed calculation unit is suitable for calculating the average value of the actual speed of the piston in the preset displacement range; an actual flow rate calculation unit adapted to calculate a product of the actual speed average value and a sectional area of the clutch actuator oil chamber as the actual flow rate; a ratio calculation unit adapted to calculate a ratio between the target flow rate and the actual flow rate as the flow compensation point.
Optionally, the actual speed calculating unit includes: the average rolling filtering unit is suitable for carrying out average rolling filtering on the actual displacement time curve of the piston in the preset displacement range; a slope calculation unit adapted to calculate a slope of the average roll filtered displacement time curve; and the low-pass filtering unit is suitable for performing low-pass filtering on the slope to obtain the actual speed average value.
Optionally, the flow compensation device of the flow variable force solenoid valve further includes a flow compensation point detection unit adapted to determine that the flow compensation point is within a preset range.
Optionally, the target flow setting unit is adapted to set different target flows within a flow range of the flow variable force solenoid valve.
Optionally, the flow compensation device of the flow variable force solenoid valve further comprises a test environment determination unit, which is adapted to determine that the pressure of the main oil path of the flow variable force solenoid valve exceeds a preset value, and the shift fork corresponding to the oil cylinder of the clutch actuator is located at a middle position.
Optionally, the oil cavity of the clutch actuator is located in a clutch of the double-clutch transmission, in which a corresponding shift fork is located in the middle position.
Compared with the prior art, the technical scheme of the embodiment of the invention has the following beneficial effects:
the flow compensation point corresponding to the target flow can be obtained through the moving state of the piston of the oil cavity of the clutch actuator, the target flow and the sectional area of the oil cavity of the clutch actuator, and flow compensation is carried out on the flow variable force electromagnetic valve according to the flow compensation point, so that the compensated flow is consistent with the target flow, and the accurate control of the clutch can be realized.
Drawings
FIG. 1 is a flow chart of a flow compensation method for a flow variable force solenoid valve according to an embodiment of the present invention;
FIG. 2 is a schematic diagram of pressure, flow and clutch position of a flow variable force solenoid valve in an embodiment of the present invention;
FIG. 3 is a flowchart of one specific implementation of step S12 in FIG. 1;
FIG. 4 is a flowchart of one specific implementation of step S31 in FIG. 3;
FIG. 5 is a schematic structural diagram of a flow compensation device of a flow variable force solenoid valve according to an embodiment of the present invention;
fig. 6 is a schematic structural diagram of a specific implementation of the compensation point calculating unit 52 in fig. 5.
Detailed Description
As previously mentioned, a Variable flow Force Solenoid (Q-VFS) valve may be used to control the clutch. Generally, the flow control of the flow variable force solenoid valve can be realized by changing a control signal of the flow variable force solenoid valve to obtain a target flow, so that the clutch can be controlled. However, during application, there is a problem that the actual flow rate does not match the target flow rate, which in turn leads to a problem that the control of the clutch is inaccurate.
In the embodiment of the invention, the flow compensation point corresponding to the target flow can be obtained through the moving state of the piston of the oil cavity of the clutch actuator, the target flow and the sectional area of the oil cavity of the clutch actuator, and the flow compensation is carried out on the flow variable force electromagnetic valve according to the flow compensation point, so that the compensated flow is consistent with the target flow, and the accurate control on the clutch can be realized.
In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in detail below.
Fig. 1 is a flowchart of a flow compensation method for a flow variable force solenoid valve according to an embodiment of the present invention, which may specifically include the following steps:
step S11, setting a target flow of the flow variable force solenoid valve, so that a piston of an oil chamber of the clutch actuator moves under the action of the flow variable force solenoid valve;
step S12, in a preset displacement range, according to the moving state of the piston, the target flow and the sectional area of the oil cavity of the clutch actuator, calculating a flow compensation point corresponding to the target flow, wherein the flow compensation point indicates the relation between the target flow and the actual flow;
and step S13, performing flow compensation on the flow variable force electromagnetic valve according to the flow compensation point.
Wherein the target flow rate may be a flow rate value within a flow rate range of the flow rate variable force solenoid valve. Since the compensation points may be different according to different target flow rates, in a specific implementation, the step S11 may set different values of the target flow rate to obtain the compensation points corresponding to different values of the target flow rate, so as to make the compensation of the variable force solenoid more specific.
Fig. 2 is a schematic diagram of pressure, flow and clutch position of a flow variable force solenoid valve according to an embodiment of the present invention, which is further described with reference to fig. 2.
The flow rate of the flow rate variable force solenoid valve can be controlled by the pressure, and in an ideal case, there should be a corresponding relationship between the target pressure and the target flow rate, as shown by a curve 1 indicating the target pressure and a curve 2 indicating the target flow rate in fig. 2. The axis of abscissa in fig. 2 is the time axis, and the axis of ordinate indicates only the direction in which the different curves increase in value, taking the direction of the arrow as the direction.
In the ideal case, the target flow rate and the actual flow rate are identical; however, in actual use, the hydraulic system where the flow variable force solenoid valve is located may have problems such as leakage, and the situation that the actual flow is inconsistent with the target flow often occurs.
In order to realize accurate control of the clutch, the flow of the flow variable force solenoid valve needs to be compensated, which requires measuring the actual flow of the flow variable force solenoid valve. The aim of compensation is to realize accurate control of the clutch, and the condition that a hydraulic system where the flow variable force electromagnetic valve is located is likely to leak and the like can influence the final control of the clutch, so that the actual flow acting on the clutch is taken as the actual flow, and the relation between the target flow and the actual flow which plays a control role on the clutch can be better reflected. Therefore, after the compensation point is calculated and obtained based on the relation, the flow compensation can be more accurately carried out on the flow variable force solenoid valve by utilizing the compensation point, and the accuracy of controlling the clutch can be further improved.
The flow actually acting on the clutch is injected into the oil cavity of the clutch actuator, and the piston of the oil cavity of the clutch actuator is pushed to act, so that the control of the clutch is completed. Therefore, the relationship between the target flow and the actual flow can be obtained by measuring the moving state of the piston and combining the sectional area of the oil cavity of the clutch actuator so as to calculate the compensation point.
The preset displacement range in step S12 may be a displacement of the piston within a period of time after the target flow rate is set, and the moving state of the piston is stable within the preset displacement range. Such as the region between points T1 and T2 in fig. 2. The curve 3 is the displacement time curve of the piston, and it can be seen that the moving state of the piston is relatively stable in this region.
Fig. 3 is a flowchart of an implementation of step S12 in fig. 1, and step S12 in fig. 1 is further described below with reference to fig. 3.
Step S12 in fig. 1 may include the following steps:
step S31, calculating the average value of the actual speed of the piston in the preset displacement range;
step S32, calculating the product of the actual speed average value and the sectional area of the oil cavity of the clutch actuator as the actual flow;
step S33, calculating a ratio between the target flow rate and the actual flow rate as the flow rate compensation point.
Wherein, referring to fig. 4, the step S31 of fig. 3 of calculating the actual speed of the piston movement may include the following steps:
step S41, carrying out average rolling filtering on the actual displacement time curve of the piston in the preset displacement range;
step S42, calculating the slope of the displacement time curve after the average rolling filtration;
step S43, low-pass filtering the slope to obtain the actual speed average.
The actual displacement time curve of the piston can be obtained based on the sensor, clutter and jumping may exist in an electric signal output by the sensor, so that after the actual displacement time curve is smoothed, the slope is obtained, and the result is accurate.
In a specific implementation, before step S13 in fig. 1, the method may further include: and determining that the flow compensation point is within a preset range. The preset range may be empirical data. If the calculated flow compensation point is beyond the preset range, it usually indicates that the clutch is in an unstable motion state, such as a clutch stuck or a position jump, and the like, at this time, the compensation point data may be discarded, and step S11 in fig. 1 is executed again.
When the pressure of the main oil path of the flow variable force solenoid valve exceeds a preset value, and the vehicle is in a stable driving state and there is no need for a gear shift, the method for compensating the flow of the flow variable force solenoid valve according to the embodiment of the present invention may obtain a more accurate result, so before step S11 shown in fig. 1, the method may further include: and determining that the pressure of a main oil way of the flow variable-force electromagnetic valve exceeds a preset value, and the gear shifting fork corresponding to the oil cylinder of the clutch actuator is located at the middle position.
In specific implementation, the oil cavity of the clutch actuator is located in a clutch of which a corresponding shift fork in the dual clutch transmission is located at a middle position, and the situation that the shift fork corresponding to the oil cylinder of the clutch actuator is located at the middle position can include the following situations:
when the vehicle stably runs on an odd gear, all the shifting forks on an even shaft are disengaged to a middle position, at the moment, the flow variable force electromagnetic valves corresponding to the even clutches can be controlled to be in a target flow, and other valve bodies matched with the flow variable force electromagnetic valves corresponding to the even clutches are controlled to be in a corresponding target state, for example, a Pressure variable force Solenoid valve (P-VFS) is controlled to be in a target state matched with the target flow;
when the vehicle stably runs on even gears, all the shifting forks on the odd shafts are disengaged to the middle position, the Q-VFS of the odd clutches can be controlled to be in a target flow, and other valve bodies matched with the flow variable force electromagnetic valves corresponding to the odd clutches are controlled to be in a corresponding target state.
Therefore, the embodiment of the invention can be implemented in the normal running process of the vehicle, and only the gear shifting fork corresponding to the flow variable force electromagnetic valve to be compensated is located at the middle position, namely the clutch corresponding to the flow variable force electromagnetic valve to be compensated does not output torque through the gearbox.
The flow compensation method in the embodiment of the invention can be implemented in the process of testing after the vehicle is off-line, and also can be implemented in the process of normal use of the vehicle when the number of gear shifting times reaches a preset value or the driving mileage of the vehicle where the flow variable force electromagnetic valve is located reaches a preset value.
According to the embodiment of the invention, the flow compensation point corresponding to the target flow can be obtained through the moving state of the piston of the oil cavity of the clutch actuator, the target flow and the sectional area of the oil cavity of the clutch actuator, and the flow compensation is carried out on the flow variable force electromagnetic valve according to the flow compensation point, so that the compensated flow is consistent with the target flow, and the accurate control on the clutch can be realized.
The embodiment of the present invention further provides a flow compensation device for a flow variable force solenoid valve, and a schematic structural diagram of the flow compensation device is shown in fig. 5, which specifically includes:
a target flow rate setting unit 51 adapted to set a target flow rate of the flow rate variable force solenoid valve so that a piston of the oil chamber of the clutch actuator moves under the action of the flow rate variable force solenoid valve;
a compensation point calculation unit 52 adapted to calculate a flow compensation point corresponding to the target flow according to the moving state of the piston, the target flow and the sectional area of the oil chamber of the clutch actuator within a preset displacement range, wherein the flow compensation point indicates the relationship between the target flow and the actual flow;
and the flow compensation unit 53 is suitable for performing flow compensation on the flow variable force electromagnetic valve according to the flow compensation point.
In a specific implementation, the target flow setting unit 51 is adapted to set different target flow rates within the flow range of the flow variable force solenoid valve.
Referring to fig. 6, wherein the compensation point calculating unit 52 in fig. 5 may include:
an actual speed calculation unit 61 adapted to calculate an average value of the actual speeds of the piston movements within the preset displacement range;
an actual flow rate calculation unit 62 adapted to calculate a product of the actual speed average and a cross-sectional area of the clutch actuator oil chamber as the actual flow rate;
a ratio calculation unit 63 adapted to calculate a ratio between the target flow rate and the actual flow rate as the flow compensation point.
In a specific implementation, the actual speed calculation unit 61 may include:
an average rolling filtering unit (not shown) adapted to perform average rolling filtering on an actual displacement time curve of the piston within the preset displacement range;
a slope calculation unit (not shown) adapted to calculate the slope of the average rolling filtered displacement time curve;
a low pass filtering unit (not shown) adapted to low pass filter the slope to obtain the actual speed average.
In a specific implementation, the flow compensation device of the flow variable force solenoid valve in the embodiment of the present invention may further include: and a flow compensation point detection unit (not shown) adapted to determine that the flow compensation point is within a preset range.
In a specific implementation, the flow compensation device of the flow variable force solenoid valve in the embodiment of the present invention may further include: and the test environment determining unit (not shown) is suitable for determining that the pressure of a main oil path of the flow variable force electromagnetic valve exceeds a preset value, and a gear shifting fork corresponding to the oil cylinder of the clutch actuator is positioned in a middle position.
In specific implementation, the clutch actuator oil chamber is located in a clutch of a double-clutch transmission with a corresponding shift fork in a middle position.
The various elements of the flow compensation apparatus of a flow variable force solenoid valve in embodiments of the present invention may be implemented or performed with a general purpose processor, a Digital Signal Processor (DSP), an Application Specific Integrated Circuit (ASIC), a Field Programmable Gate Array (FPGA) or other programmable logic device, discrete gate or transistor logic, discrete hardware components, or any combination thereof designed to perform the functions described herein, in conjunction with a sensing device, such as a position sensor. A general purpose processor may be a microprocessor, but in the alternative, the processor may be any conventional processor, controller, microcontroller, or state machine. A processor may also be implemented as a combination of computing devices, e.g., a combination of a DSP and a microprocessor, a plurality of microprocessors, one or more microprocessors in conjunction with a DSP core, or any other such configuration.
Those skilled in the art will appreciate that all or part of the steps in the methods of the above embodiments may be implemented by associated hardware instructed by a program, which may be stored in a computer-readable storage medium, and the storage medium may include: ROM, RAM, magnetic or optical disks, and the like.
Although the present invention is disclosed above, the present invention is not limited thereto. Various changes and modifications may be effected therein by one skilled in the art without departing from the spirit and scope of the invention as defined in the appended claims.
Claims (12)
1. A flow compensation method of a flow variable force electromagnetic valve is characterized by comprising the following steps:
setting a target flow of a flow variable force electromagnetic valve, so that a piston of an oil cavity of a clutch actuator moves under the action of the flow variable force electromagnetic valve;
in a preset displacement range, according to the moving state of the piston, the target flow and the sectional area of an oil cavity of the clutch actuator, calculating a flow compensation point corresponding to the target flow, wherein the flow compensation point indicates the relation between the target flow and the actual flow; wherein the actual flow rate is the flow rate actually acting on the clutch;
carrying out flow compensation on the flow variable force electromagnetic valve according to the flow compensation point;
wherein the obtaining of the flow compensation point corresponding to the target flow comprises:
calculating the average value of the actual speed of the piston in the preset displacement range;
calculating the product of the actual speed average value and the sectional area of the oil cavity of the clutch actuator as the actual flow;
calculating a ratio between the target flow rate and the actual flow rate as the flow compensation point.
2. The method of flow compensation for a flow variable force solenoid valve as recited in claim 1 wherein calculating an average of actual speeds at which said piston moves comprises:
carrying out average rolling filtering on the actual displacement time curve of the piston in the preset displacement range;
calculating the slope of the displacement time curve after the average rolling filtration;
low pass filtering the slope to obtain the actual speed average.
3. The method for flow compensation of a variable flow solenoid valve according to claim 1, wherein before performing flow compensation of the variable flow solenoid valve according to the flow compensation point, the method further comprises: and determining that the flow compensation point is within a preset range.
4. The method of flow compensation of a flow variable force solenoid valve as claimed in claim 1 wherein said setting a target flow of a flow variable force solenoid valve comprises: and setting different target flow rates within the flow range of the flow variable force electromagnetic valve.
5. The method for flow compensation of a flow variable force solenoid valve according to any one of claims 1 to 4, wherein before setting the target flow of the flow variable force solenoid valve, the method further comprises: and determining that the pressure of a main oil way of the flow variable-force electromagnetic valve exceeds a preset value, and a gear shifting fork corresponding to an oil cavity of the clutch actuator is located at a middle position.
6. The method for flow compensation of a flow variable force solenoid valve as claimed in any one of claims 1 to 4 wherein said clutch actuator oil chamber is located in the clutch with the corresponding shift fork in the center position in a dual clutch transmission.
7. A flow compensation device of a flow variable force electromagnetic valve is characterized by comprising:
the target flow setting unit is suitable for setting the target flow of the flow variable force electromagnetic valve, so that a piston of an oil cavity of the clutch actuator moves under the action of the flow variable force electromagnetic valve;
the compensation point calculation unit is suitable for calculating a flow compensation point corresponding to the target flow according to the moving state of the piston, the target flow and the sectional area of an oil cavity of the clutch actuator in a preset displacement range, and the flow compensation point indicates the relation between the target flow and the actual flow; wherein the actual flow rate is the flow rate actually acting on the clutch;
the flow compensation unit is suitable for carrying out flow compensation on the flow variable force electromagnetic valve according to the flow compensation point;
wherein the compensation point calculating unit includes:
the actual speed calculation unit is suitable for calculating the average value of the actual speed of the piston in the preset displacement range;
an actual flow rate calculation unit adapted to calculate a product of the actual speed average value and a sectional area of the clutch actuator oil chamber as the actual flow rate;
a ratio calculation unit adapted to calculate a ratio between the target flow rate and the actual flow rate as the flow compensation point.
8. The flow rate compensation device of a flow rate variable force solenoid valve according to claim 7, wherein the actual speed calculation unit includes:
the average rolling filtering unit is suitable for carrying out average rolling filtering on the actual displacement time curve of the piston in the preset displacement range;
a slope calculation unit adapted to calculate a slope of the average roll filtered displacement time curve;
and the low-pass filtering unit is suitable for performing low-pass filtering on the slope to obtain the actual speed average value.
9. The flow compensating device of a flow variable force solenoid valve according to claim 7, further comprising a flow compensation point detecting unit adapted to determine that the flow compensation point is within a preset range.
10. The flow compensating device of a flow variable force solenoid valve according to claim 7, wherein the target flow setting unit is adapted to set different target flow rates within a flow range of the flow variable force solenoid valve.
11. The flow compensating device of the flow variable force solenoid valve according to any one of claims 7 to 10, further comprising a test environment determining unit adapted to determine that the pressure of the main oil passage of the flow variable force solenoid valve exceeds a preset value and the shift fork corresponding to the oil chamber of the clutch actuator is located at a neutral position.
12. The flow compensating device of a flow variable force solenoid valve as claimed in any one of claims 7 to 10, wherein the clutch actuator oil chamber is located in a clutch of a dual clutch transmission with a corresponding shift fork in a neutral position.
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| CN201710329889.1A CN108869839B (en) | 2017-05-11 | 2017-05-11 | Flow compensation method and device of flow variable force electromagnetic valve |
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| CN201710329889.1A CN108869839B (en) | 2017-05-11 | 2017-05-11 | Flow compensation method and device of flow variable force electromagnetic valve |
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| CN112268696B (en) * | 2020-10-14 | 2022-06-21 | 安徽江淮汽车集团股份有限公司 | Clutch detection method, device, storage medium and device |
| CN115711315A (en) * | 2021-08-23 | 2023-02-24 | 维谛技术有限公司 | Valve opening control method and device, nonvolatile storage medium and processor |
| CN115854021A (en) * | 2022-12-13 | 2023-03-28 | 中国第一汽车股份有限公司 | Control method and device for hydraulic system solenoid valve, vehicle and storage medium |
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| CN102520293A (en) * | 2011-12-28 | 2012-06-27 | 北京博格华纳汽车传动器有限公司 | Production test method for force-variable electromagnetic valve of automatic transmission |
| CN104024659A (en) * | 2011-12-28 | 2014-09-03 | 日立建机株式会社 | Power regeneration device for work machine and work machine |
| CN103629341A (en) * | 2013-12-13 | 2014-03-12 | 安徽江淮汽车股份有限公司 | Wet-type double-clutch automatic transmission electromagnetic valve characteristic curve compensation method |
| CN104316316A (en) * | 2014-08-19 | 2015-01-28 | 盛瑞传动股份有限公司 | Testing method and system of speed changer |
| CN105673837A (en) * | 2016-04-14 | 2016-06-15 | 安徽江淮汽车股份有限公司 | Method and system for controlling electromagnetic valves of double-clutch automatic transmission |
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