CN110425275B - Transmission gear shifting control method - Google Patents

Transmission gear shifting control method Download PDF

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CN110425275B
CN110425275B CN201910681636.XA CN201910681636A CN110425275B CN 110425275 B CN110425275 B CN 110425275B CN 201910681636 A CN201910681636 A CN 201910681636A CN 110425275 B CN110425275 B CN 110425275B
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gear
shifting
control valve
pressure
neutral
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CN110425275A (en
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顾强
叶珂羽
陈建勋
刘振宇
梁伟朋
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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
    • 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
    • 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
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/32—Gear shift yokes, e.g. shift forks
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/40—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism comprising signals other than signals for actuating the final output mechanisms
    • 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
    • F16H61/0021—Generation or control of line pressure
    • F16H2061/0034—Accumulators for fluid pressure supply; Control thereof
    • 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
    • F16H2061/0043—Cleaning of hydraulic parts, e.g. removal of an orifice clogging

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Transmission Device (AREA)
  • Gear-Shifting Mechanisms (AREA)

Abstract

The invention belongs to the technical field of automobiles, and discloses a transmission gear-shifting control method. The transmission shift control method includes: in the gear-off stage, a gear-shifting piston of a gear-shifting hydraulic cylinder is configured to drive a shifting fork to move relative to the gear-shifting hydraulic cylinder by adjusting a gear-shifting pressure control valve and a flow control valve, so that the shifting fork pushes a synchronizer to realize the gear shifting of the transmission to a neutral gear; and in the neutral gear taking-in stage, the shifting pressure control valve and the flow control valve are adjusted according to the current position of the shifting fork and the neutral gear target position of the shifting fork, so that the shifting fork enters the neutral gear target position of the shifting fork. The mode of pressure and flow combined control is adopted, the hydraulic system in the hydraulic actuating mechanism is matched, the transmission is quickly and accurately picked, and the requirement of quick gear shifting of the transmission is met. According to the current position and the neutral target position of the shifting fork, the shifting pressure control valve and the shifting flow control valve are adjusted to quickly and accurately pick up the gear, the overall gear shifting time is shortened, the reliability and the speed of gear shifting are guaranteed, and the gear shifting quality is improved.

Description

Transmission gear shifting control method
Technical Field
The invention relates to the technical field of automobiles, in particular to a transmission gear-shifting control method.
Background
With the widespread use of automobiles, drivers have made higher demands on the convenience of automobile handling. The vehicle adopting the automatic transmission can replace a driver to automatically complete operations such as vehicle starting, gear shifting and the like, and the driving intensity and the driving technical requirements of the driver are reduced. Compared with a manual transmission, the automatic transmission has better driving smoothness and is popular, so that the market occupancy rate of vehicles carrying the automatic transmission is continuously improved in recent years.
In the gear shifting process of the automatic transmission, the current gear is shifted back to the neutral gear, which is one of operations greatly influencing the gear shifting process, and the failure of gear shifting can directly cause the failure of gear shifting. The gear shifting operation of the transmission is mainly completed by a hydraulic actuating mechanism or an electric actuating mechanism. Transmission hydraulic actuation systems have been developed to provide leakage systems that have significantly improved drive efficiency over previous systems. Aiming at a novel hydraulic system, the reliability and the speed of gear shifting cannot be ensured by utilizing the existing control method, so that the gear shifting quality is poor.
Disclosure of Invention
The invention aims to provide a transmission gear shifting control method which is used for quickly and accurately picking up a gear so as to improve the gear shifting quality.
In order to achieve the purpose, the invention adopts the following technical scheme:
a transmission shift control method, characterized by comprising:
in the gear-off stage, a gear-shifting piston of a gear-shifting hydraulic cylinder is configured to drive a shifting fork to move relative to the gear-shifting hydraulic cylinder by adjusting a gear-shifting pressure control valve and a flow control valve, so that the shifting fork pushes a synchronizer to realize the gear shifting of the transmission to a neutral gear;
and a neutral gear taking-in stage, adjusting a gear shifting pressure control valve and a flow control valve according to the current position of the shifting fork and the neutral gear target position of the shifting fork, and enabling the shifting fork to enter the neutral gear target position of the shifting fork.
Preferably, a limiting frame is arranged on the shifting fork, a limiting ball is pressed on the limiting frame through an elastic piece and can be matched with the surface of the limiting frame in a rolling manner, the gear shifting piston is connected to an inverted cone, and the inverted cone selectively abuts against the inverted cone of the gear ring;
and in the gear-off stage, adjusting the pressure P of the gear-shifting pressure control valve to be P1+ P2, wherein P1 is the pressure applied to the gear-shifting piston to enable the limiting ball to move out of the bottom of the limiting frame, and P2 is the pressure applied to the gear-shifting piston to enable the back taper of the synchronizer to be separated from the back taper of the gear ring.
Preferably, P1 is F1/a, where F1 is the pressure applied to the shift piston to move the limit ball out of the bottom of the limit bracket, a is the effective acting area of the shift piston, and F1 is calculated from the coefficient of friction between the limit ball and the limit bracket, the diameter of the limit ball, the pre-compression amount of the elastic member, and the relative position of the limit ball and the limit bracket.
Preferably, P2 is F2/a, where F2 is the pressure exerted on the shift piston to disengage the synchronizer back-taper from the ring gear back-taper, a is the effective area of the shift piston, and F2 is obtained by bench calibration tests.
Preferably, when the pressure P of the shift pressure control valve is adjusted to P1+ P2 and the flow rate of the flow control valve is adjusted to Q1, if the position of the shift fork is not moved and changed, the pressure P of the shift pressure control valve is reduced to zero for T1 time, and then the pressure of the shift pressure control valve is gradually increased by Δ P as a step until the shift fork position is moved or the maximum gear-off time T is reached.
Preferably, if the current position of the shifting fork moves to a first preset position L1, entering a neutral gear extraction stage; and if the gear-picking time T reaches the maximum gear-picking time Tmax, failing to enter a neutral gear-picking stage.
Preferably, during the neutral gear extraction phase, the pressure p (x) of the shift pressure control valve is a piecewise function of the current position x of the shift fork and the neutral target position:
Figure BDA0002144965550000031
preferably, in the neutral gear extraction stage, the flow of the flow control valve is controlled and corrected by adopting PID closed-loop control according to the current position and the target neutral gear position of the shifting fork.
Preferably, the method further comprises, after the neutral gear extraction stage:
and in the neutral gear maintaining stage, continuously acquiring the current position of the shifting fork for N times at intervals of detection interval time delta T, and if the current position of the shifting fork at each time is the neutral gear target position of the shifting fork, adjusting the pressure of the shifting pressure control valve and the flow rate of the flow control valve to be zero.
Preferably, an oil filling stage is further included before the gear disengaging stage, the preset pressure P0 of the gear shifting pressure control valve and the preset flow Q0 of the flow control valve are obtained and set, then the hydraulic oil is filled into the gear shifting hydraulic cylinder, and the time T of the oil filling stage is not less than the preset time T0.
The invention has the beneficial effects that:
according to the gear shifting control method of the transmission, the gear shifting piston of the gear shifting hydraulic cylinder is configured to drive the shifting fork to move relative to the gear shifting hydraulic cylinder by adjusting the gear shifting pressure control valve and the flow control valve, so that the shifting fork pushes the synchronizer to realize the gear shifting of the transmission to be in a neutral gear, and the hydraulic system in the hydraulic actuating mechanism is matched in a pressure and flow combined control mode, so that the transmission can be quickly and accurately picked up, and the requirement of quick gear shifting of the transmission is met. Meanwhile, according to the current position and the neutral target position of the shifting fork, the shifting pressure control valve and the flow control valve are adjusted, so that the shifting fork enters the neutral target position of the shifting fork, the shifting can be quickly and accurately picked, the overall shifting time is shortened, the reliability and the speed of shifting are ensured, and the shifting quality is improved.
Drawings
FIG. 1 is a hydraulic schematic of a hydraulic actuator controlled by the transmission shift control method of the present invention;
FIG. 2 is a schematic diagram of the hydraulic actuator connections controlled by the transmission shift control method provided in accordance with the present invention;
FIG. 3 is a schematic diagram of a spacing bracket and a spacing ball in a transmission shift control method provided in accordance with the present invention;
FIG. 4 is a flow chart of a transmission shift control method provided by the present invention;
FIG. 5 is a functional block diagram of a proportional-integral control method implemented in accordance with the present invention for providing a transmission shift control method.
In the figure:
1. a hydraulic source; 2. a shift pressure control valve; 3. a flow control valve; 4. a shift hydraulic cylinder; 5. a shifting fork; 6. an accumulator; 7. a limiting frame; 8. a limiting ball; 9. an elastic member; 10. a filter; 11. a position sensor;
41. a shift piston;
71. an arc-shaped bulge; 72. and a limiting groove.
Detailed Description
In order to make the technical problems solved, technical solutions adopted and technical effects achieved by the present invention clearer, the technical solutions of the embodiments of the present invention will be described in further detail below with reference to the accompanying drawings, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all 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.
In the description of the present invention, unless expressly stated or limited otherwise, the terms "connected," "connected," and "fixed" are to be construed broadly, e.g., as meaning permanently connected, removably connected, or integral to one another; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
In the present invention, unless otherwise expressly stated or limited, "above" or "below" a first feature means that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact with each other via another feature therebetween. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.
The technical scheme of the invention is further explained by the specific implementation mode in combination with the attached drawings.
In the gear shifting process of the automatic transmission, the current gear is shifted back to the neutral gear, which is one of operations greatly influencing the gear shifting process, and the failure of gear shifting can directly cause the failure of gear shifting. Therefore, the embodiment provides a gear shifting control method of the transmission, which is used for completing gear shifting operation of the transmission by controlling a hydraulic actuator. As shown in fig. 1, the hydraulic actuator includes a hydraulic source 1, a shifting pressure control valve 2, a flow control valve 3, a shifting hydraulic cylinder 4, a shifting fork 5, an accumulator 6, a limiting frame 7, a limiting ball 8, an elastic member 9 and a filter 10, the hydraulic source 1 may be a hydraulic pump, etc., the hydraulic source 1 may provide hydraulic oil of an oil tank to a hydraulic pipeline, the pressure of the shifting pressure control valve 2 is controlled by adjusting the current of the shifting pressure control valve 2, the hydraulic oil whose pressure is adjusted by the shifting pressure control valve 2 enters the flow control valve 3, the flow rate and direction of the hydraulic oil entering the shifting hydraulic cylinder 4 may be changed by adjusting the current of the flow control valve 3, and a shifting piston 41 is slidably disposed in the shifting hydraulic cylinder 4, so as to change the moving speed and direction of the shifting piston 41 of the shifting hydraulic cylinder 4. The shifting piston 41 is connected to the shifting fork 5, and along with the movement of the shifting piston 41, the shifting fork 5 also moves and pushes the synchronizer to complete the processes of gear picking and gear engaging of the transmission.
It can be understood that, in each oil inlet or return hydraulic pipeline, in order to prevent the hydraulic pipeline, the pressure control valve 2 that shifts, flow control valve 3 and the hydraulic cylinder 4 that shifts from appearing blockking up, be provided with a plurality of filters 10 on the hydraulic pipeline to impurity in the filtering hydraulic oil, in order to guarantee the cleanliness of hydraulic oil.
As shown in fig. 2-3, in order to ensure the position limitation of the shift fork 5 at the neutral position, a limiting frame 7 is arranged on the shift fork 5, the limiting frame 7 is of a chevron structure, the surface of the limiting frame 7 is of an arc structure, specifically, two arc protrusions 71 are symmetrically arranged on one side of the limiting frame 7, and a limiting groove 72 is formed between the two arc protrusions 71. Wherein, the joints between the two side surfaces of the limiting frame 7, the arc-shaped bulges 71 and the limiting grooves 72 are all transited through fillets. A position sensor 11 is provided at one side of the shift fork 5, and the position sensor 11 detects the position of the shift fork 5.
Elastic component 9 can support spacing ball 8 and press on spacing 7, and spacing ball 8 specifically is the steel ball, and elastic component 9 specifically is the spring. The position of the limiting ball 8 is kept still, the limiting frame 7 moves under the driving action of the shifting fork 5, the limiting ball 8 is matched with the surface of the limiting frame 7 in a rolling mode, the limiting ball 8 can be moved out from the bottoms of two sides of the limiting frame 7, and then rolls to enter the limiting groove 72 after passing through the arc-shaped bulge 71. When the limiting ball 8 just slides into the limiting groove 72, the shifting fork 5 is just at the neutral position. When the transmission is in neutral gear shifting, the shifting piston 41 can drive the shifting fork 5 to move by adjusting the shifting pressure control valve 2 and the flow control valve 3 so as to overcome the resistance of the elastic part 9 to the limiting ball 8, and by the mode, the buffering effect is achieved, and the accuracy and the reliability of shifting are ensured.
The transmission shift control method provided by the embodiment divides a gear-shifting process into four stages as shown in fig. 4: oil filling stage, gear picking stage, neutral gear picking stage and neutral gear maintaining stage. The control of the four stages will be described in detail below.
S1 oil filling stage
An oil temperature sensor is arranged in the oil tank and used for detecting the current oil temperature of hydraulic oil, and according to the current oil temperature, a table is looked up to obtain the preset pressure P0 of the gear shifting pressure control valve 2 and the preset flow Q0 of the flow control valve 3, wherein the table is input to the current oil temperature, the table is output to the pressure of the gear shifting pressure control valve 2 and the flow of the flow control valve 3, and numerical values of the pressure and the flow of the flow control valve 3 are determined by a calibration test. According to the numerical values obtained by table lookup, the pressure of the shift pressure control valve 2 is set to be a preset pressure P0 and the flow of the flow control valve 3 is set to be a preset flow Q0, then the shift hydraulic cylinder 4 is filled with hydraulic oil, and the gap between the shift fork 5 and the synchronizing ring is eliminated. In the process, the oil filling time T of the oil filling stage is not less than the preset time T0, and when the oil filling time exceeds the preset time T0, the gear picking stage is started.
In the embodiment, the current oil temperature is preferably 30 ℃, the preset pressure P0 of the shift pressure control valve 2 obtained after table lookup is 10bar, the preset flow Q0 of the flow control valve 3 is 10L/min, and the preset time T0 of the oil filling stage is 100 ms.
S2, gear-off stage
After entering the gear-off stage, the shifting piston 41 of the shifting hydraulic cylinder 4 is configured to drive the shifting fork 5 to move relative to the shifting hydraulic cylinder 4 by adjusting the shifting pressure control valve 2 and the flow control valve 3, so that the shifting fork 5 pushes the synchronizer to realize the gear shift of the transmission to the neutral gear. Specifically, the pressure P of the shift pressure control valve 2 is adjusted to be P1+ P2, where P1 is the pressure applied to the shift piston 41 to move the limit ball 8 out of the bottom of the limit frame 7, the shift piston 41 is connected to an inverted cone which selectively abuts against an inverted cone of the gear ring, and P2 is the pressure applied to the shift piston 41 to disengage the inverted cone of the synchronizer from the inverted cone of the gear ring.
For the determination of P1, P1 can be determined by determining F1 according to the formula P1 — F1/a. Where F1 is the pressure applied to the shift piston 41 to move the limit ball 8 out of the bottom of the limit bracket 7, and a is the effective acting area of the shift piston 41. Furthermore, the size of the F1 is related to parameters such as the friction coefficient between the limit ball 8 and the limit frame 7, the shape of the limit frame 7, the diameter of the limit ball 8, the pre-compression amount of the elastic piece 9, and the relative position between the limit ball 8 and the limit frame 7, and the manual calculation is difficult, and the numerical relationship between the size of the F1 and the relative position between the limit ball 8 and the limit frame 7 needs to be obtained by inputting the parameters into software such as Adams and ProE for calculation.
For the determination of P2, P2 can be determined by determining F2 according to the formula P2 — F2/a. Where F2 is the pressure applied to the shift piston 41 to disengage the synchronizer back-taper from the ring gear back-taper, and a is the effective active area of the shift piston 41. Alternatively, F2 was obtained directly by bench calibration testing.
When the pressure P of the shift pressure control valve 2 is adjusted to P1+ P2 and the flow of the flow control valve 3 is adjusted to Q1, the current position of the shift fork 5 is detected, if the position of the shift fork 5 is not moved and changed, the pressure P of the shift pressure control valve 2 is reduced to zero and lasts for T1 time, and then the pressure of the shift pressure control valve 2 is gradually increased by taking Δ P as a step until the position of the shift fork 5 is moved or the maximum gear-off time T is reached. If the current position of the shifting fork 5 moves to a first preset position L1, entering a neutral gear extraction stage; and if the gear-picking time T reaches the maximum gear-picking time Tmax, failing to enter a neutral gear-picking stage.
In the embodiment, preferably, according to the position of the shift fork 5, the pressure F1 of the limiting ball 8 moving out of the bottom of the limiting frame 7 is 25N, so that the pressure P1 is calculated to be 0.7bar, and the pressure P2 of the synchronizer back taper disengaging from the gear ring back taper is calculated to be 3bar, therefore, the pressure of the shift pressure control valve 2 is set to be 25.7bar, the flow Q1 of the flow control valve 3 is set to be 8L/min, and at this time, if the shift fork 5 is detected to move, when the shift fork 5 moves to the first preset position L1 to be 3.5mm, the neutral gear picking stage is entered.
In the gear picking stage, the gear shifting piston 41 of the gear shifting hydraulic cylinder 4 is configured to drive the shifting fork 5 to move relative to the gear shifting hydraulic cylinder 4 by adjusting the gear shifting pressure control valve 2 and the flow control valve 3, so that the shifting fork 5 pushes the synchronizer to realize the gear shifting of the transmission to the neutral gear, and the mode of pressure and flow combined control is adopted to match a hydraulic system in a hydraulic actuating mechanism, so that the quick and accurate gear picking of the transmission is realized, and the requirement of quick gear shifting of the transmission is met.
S3, neutral gear extraction stage
When the shift fork 5 is moved to the first preset position L1, the neutral extraction stage is entered. And dynamically adjusting the current of the pressure control valve and the current of the flow control valve 3 according to the current position of the shifting fork 5 and the neutral target position of the shifting fork 5, and respectively adjusting the pressure of the shifting pressure control valve 2 and the flow of the flow control valve 3 to enable the shifting fork 5 to enter the neutral target position of the shifting fork 5.
In this phase, the pressure of the shift pressure control valve 2 is adjusted in a pressure step manner. The current position of the shifting fork 5 is detected by using the position sensor 11, because the limiting ball 8 needs to roll in the arc-shaped protrusion 71 and the limiting groove 72 of the limiting frame 7 under the action of the limiting ball 8 and the limiting frame 7, the pulling force of the shifting fork 5 which needs to drive the limiting frame 7 to move is different in each position of the limiting frame 7, and therefore, the relation between the pressure P (x) of the shifting pressure control valve 2 and the current position x and the neutral gear target position of the shifting fork 5 is a piecewise function:
Figure BDA0002144965550000091
the pressure value in the Px and the segmentation point of the current position x of the shifting fork 5 in the segmentation function can be determined through a calibration test.
Further, in the neutral gear extraction stage, the flow of the flow control valve 3 is controlled and corrected by adopting PID closed-loop control according to the current position and the neutral gear target position of the shifting fork 5. The proportional-integral adjusts the flow of the flow control valve 3 and controls the shifting fork 5 to enter a neutral position. As shown in fig. 5, the target position of the shift fork 5 is a neutral position, the position sensor 11 detects the current position of the shift fork 5, and the difference between the target position and the current position is output to the proportional link and the integral link and calculated, and then the proportional solenoid valve control current is output, so as to complete the process of regulating the flow of the flow control valve 3 by the proportional integral method.
In the embodiment, only the first segment of the segment function is adopted, that is, according to Px being P1 x e [ x1, x2], the set pressure of the shift pressure control valve 2 is obtained to be 4bar, the P parameter in the proportional link coefficient Kp of the flow control valve 3 is 30, the i parameter in the integral link 1/Kixs is 70, and after the shift fork 5 enters the neutral position, the neutral gear extraction stage is ended, and the neutral gear keeping stage is entered.
According to the transmission gear shifting control method provided by the embodiment, the gear shifting pressure control valve 2 and the flow control valve 3 are adjusted according to the current position of the shifting fork 5 and the neutral target position of the shifting fork 5, so that the shifting fork 5 enters the neutral target position of the shifting fork 5, the gear can be quickly and accurately picked, the overall gear shifting time is shortened, the gear shifting reliability and speed are ensured, and the gear shifting quality is improved.
S4, neutral keeping stage
Acquiring the current position of the shifting fork 5 for N times continuously every detection interval time delta T, wherein the interval time delta T is preferably 100ms in the embodiment, the number of times N of continuous detection is three, if the current position of the shifting fork 5 is the neutral target position of the shifting fork 5 each time, the pressure of the gear shifting pressure control valve 2 and the flow rate of the flow control valve 3 are both adjusted to be zero, the valve core of the flow control valve 3 is kept at the middle position at the moment, and the gear picking process is finished. By adopting the mode, the shifting fork 5 is ensured to be positioned at the neutral gear target position, and the reliability and the success rate of gear shifting are ensured.
In the description herein, it is to be understood that the terms "upper", "lower", "right", and the like are based on the orientations and positional relationships shown in the drawings and are used for convenience in description and simplicity in operation, but do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed in a particular orientation, and be constructed in a particular operation, and thus should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used merely for descriptive purposes and are not intended to have any special meaning.
In the description herein, references to the description of "an embodiment," "an example" or the like are intended to mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example.
In addition, the foregoing is only the preferred embodiment of the present invention and the technical principles applied. It will be understood by those skilled in the art that the present invention is not limited to the particular embodiments described herein, but is capable of various obvious changes, rearrangements and substitutions as will now become apparent to those skilled in the art without departing from the scope of the invention. Therefore, although the present invention has been described in greater detail by the above embodiments, the present invention is not limited to the above embodiments, and may include other equivalent embodiments without departing from the spirit of the present invention, and the scope of the present invention is determined by the scope of the appended claims.

Claims (2)

1. A transmission shift control method, characterized by comprising:
in the gear-off stage, a gear-shifting piston (41) of a gear-shifting hydraulic cylinder (4) is configured to drive a shifting fork (5) to move relative to the gear-shifting hydraulic cylinder (4) by adjusting a gear-shifting pressure control valve (2) and a flow control valve (3), so that the shifting fork (5) pushes a synchronizer to realize that the gear of the transmission is switched to a neutral gear;
in the neutral gear taking-in stage, according to the current position of the shifting fork (5) and the neutral gear target position of the shifting fork (5), the shifting pressure control valve (2) and the flow control valve (3) are adjusted to enable the shifting fork (5) to enter the neutral gear target position; a limiting frame (7) is arranged on the shifting fork (5), a limiting ball (8) is pressed on the limiting frame (7) through an elastic piece (9) and can be matched with the surface of the limiting frame (7) in a rolling manner, a gear shifting piston (41) is connected to an inverted cone, and the inverted cone selectively abuts against the inverted cone of the gear ring;
in the gear-off stage, adjusting the pressure P of the gear-shifting pressure control valve (2) to P1+ P2, wherein P1 is the pressure applied to the gear-shifting piston (41) to move the limiting ball (8) out of the bottom of the limiting frame (7), and P2 is the pressure applied to the gear-shifting piston (41) to separate the inverted cone of the synchronizer from the inverted cone of the gear ring;
when the pressure P of the shifting pressure control valve (2) is adjusted to P1+ P2 and the flow of the flow control valve (3) is adjusted to Q1, if the position of the shifting fork (5) is not moved and changed, the pressure P of the shifting pressure control valve (2) is reduced to zero and lasts for T1 time, and then the pressure of the shifting pressure control valve (2) is gradually increased by taking deltap as a step until the position of the shifting fork (5) is moved or the maximum gear-off time T is reached;
if the current position of the shifting fork (5) moves to a first preset position L1, entering a neutral gear extraction stage; if the gear-picking time T reaches the maximum gear-picking time Tmax, the neutral gear-picking stage is failed to enter;
after the neutral extraction phase, the method further comprises the following steps:
in the neutral gear maintaining stage, the current position of the shifting fork (5) is continuously obtained for N times at intervals of detection interval time delta T, and if the current position of the shifting fork (5) is the neutral gear target position of the shifting fork (5) each time, the pressure of the gear shifting pressure control valve (2) and the flow rate of the flow control valve (3) are adjusted to be zero; p1 ═ F1/a, where F1 is the pressure applied to the shift piston (41) to move the limit ball (8) out of the bottom of the limit carrier (7), a is the effective acting area of the shift piston (41), and F1 is calculated from the friction coefficient between the limit ball (8) and the limit carrier (7), the diameter of the limit ball (8), the pre-compression amount of the elastic member (9), and the relative position of the limit ball (8) and the limit carrier (7); p2 ═ F2/a, where F2 is the pressure exerted on the shift piston (41) to disengage the synchronizer back-taper from the ring gear back-taper, a is the effective active area of the shift piston (41), and F2 was obtained by bench calibration tests; in the neutral gear extraction stage, the relation between the pressure P (x) of the gear shifting pressure control valve (2) and the current position x and the neutral gear target position of the shifting fork (5) is a piecewise function:
Figure FDA0003286444510000021
and an oil filling stage is further included before the gear disengaging stage, the preset pressure P0 of the gear shifting pressure control valve (2) and the preset flow Q0 of the flow control valve (3) are obtained and set, then the hydraulic oil is filled into the gear shifting hydraulic cylinder (4), and the time T of the oil filling stage is not less than the preset time T0.
2. Transmission shift control method according to claim 1, characterized in that in the neutral extraction phase, the flow of the flow control valve (3) is controlled and corrected using PID closed loop control, according to the current position of the fork (5) and the target neutral position.
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