CN113464586A - Wet clutch protection system and method based on hydraulic mechanical continuously variable transmission - Google Patents
Wet clutch protection system and method based on hydraulic mechanical continuously variable transmission Download PDFInfo
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- CN113464586A CN113464586A CN202110858539.0A CN202110858539A CN113464586A CN 113464586 A CN113464586 A CN 113464586A CN 202110858539 A CN202110858539 A CN 202110858539A CN 113464586 A CN113464586 A CN 113464586A
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/123—Details not specific to one of the before-mentioned types in view of cooling and lubrication
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/10—System to be controlled
- F16D2500/104—Clutch
- F16D2500/10443—Clutch type
- F16D2500/1045—Friction clutch
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/10—System to be controlled
- F16D2500/11—Application
- F16D2500/1107—Vehicles
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/305—Signal inputs from the clutch cooling
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/50—Problem to be solved by the control system
- F16D2500/502—Relating the clutch
- F16D2500/50296—Limit clutch wear
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
The application relates to and provides a wet clutch protection system and method based on a hydraulic mechanical continuously variable transmission, which are used for solving the problem that safe running of equipment is affected when the equipment encounters severe sliding abrasion in a severe working environment in the related art. Carry out cooling and lubrication to the clutch under clutch shift state and combination state in this application, and do not carry out cooling and lubrication to it when the clutch is in the disengagement state, can guarantee to carry out cooling and lubrication as required from this, only play the effect when the gear shift process is with the state of shelves promptly, effectively improved the efficiency of cooling and lubrication oil circuit. In addition, in the embodiment of the application, when the gear shifting state is carried out, the controller can analyze the friction work, and when the friction work of the clutch exceeds a corresponding threshold, the clutch protection measure is started, so that when the heat generated by the sliding friction far exceeds the cooling lubricating system, the wear failure or ablation of the clutch can be avoided as far as possible, and the safety performance of the equipment is improved.
Description
Technical Field
The application relates to the technical field of high-horsepower hydraulic mechanical stepless speed change equipment, in particular to a wet clutch protection system and method based on a hydraulic mechanical stepless speed change box.
Background
The prior art protects the sliding wear condition of the clutch under different working conditions by increasing the cooling and lubricating flow, the method is effective for vehicles with stable working conditions, but for equipment which often operates under the condition of complex environment and variable working conditions, when the equipment encounters a severe operating environment, a large external operating load can cause the clutch of the gearbox to generate severe sliding wear, the heat generated by the sliding wear far exceeds the protection capability of a cooling and lubricating system, the clutch is not protected by increasing the cooling and lubricating flow, and even the abrasion failure or ablation of the clutch is caused in severe conditions, so that the safe running of the equipment is influenced.
Disclosure of Invention
The embodiment of the application provides a wet clutch protection system and method based on a hydraulic mechanical continuously variable transmission, which are used for solving the problem that in the related art, when the equipment meets a severe operating environment, a large external operating load can cause the transmission clutch to generate serious sliding friction to influence the safe running of the equipment.
In a first aspect, the present application provides a wet clutch protection system based on a hydraulic mechanical continuously variable transmission, including an oil supply device, a clutch control oil path, a clutch cooling and lubricating oil path and a controller, wherein:
the oil supply device is used for supplying oil to the clutch control oil way and the clutch cooling and lubricating oil way;
the clutch control oil way is used for controlling oil to enter the clutch control oil cylinder when the clutch is in a gear shifting state and controlling the clutch cooling and lubricating oil way to cool and lubricate the clutch; when the clutch is in a separation state, controlling the clutch cooling and lubricating oil path to stop cooling and lubricating the clutch;
the clutch cooling lubricating oil path is also used for continuously providing lubricating oil to cool and lubricate the clutch in the combining process of the clutch;
the controller is used for determining the friction work of the clutch when the clutch is in a gear shifting state, and starting a clutch protection measure when the friction work of the clutch exceeds a corresponding threshold.
Optionally, the clutch control oil passage includes: system pump, electromagnetism proportional valve and clutch control hydro-cylinder, wherein:
when the clutch enters a gear shifting state, the electromagnetic proportional valve is electrified, and the valve core of the electromagnetic valve is gradually opened until the valve core reaches the maximum opening degree;
and the system pump controls oil to enter the clutch control oil cylinder through the electromagnetic proportional valve to control the clutch to be combined.
Optionally, the friction work comprises actual friction work per unit time;
the clutch control oil passage further includes: the pressure sensor is arranged between the electromagnetic proportional valve and the control oil cylinder and used for providing a pressure value for the controller;
the controller is specifically configured to determine the actual friction work according to the pressure value and the unit time.
Optionally, the clutch cooling and lubricating oil path includes a lubricating pump, a cooler, a temperature control valve and a lubricating valve, and the oil provided to the clutch cooling and lubricating oil path includes oil of the first branch and oil of the second branch, wherein:
when the oil temperature is lower than the temperature threshold value, the temperature control valve is closed, the oil liquid of the first branch flows to the lubricating valve through the cooler, and the oil liquid of the second branch bypasses the cooler and flows to the lubricating valve;
when the oil temperature is higher than or equal to a temperature threshold value, the temperature control valve is opened, and all the oil in the first branch and the oil in the second branch flow to the lubricating valve after flowing through the cooler for cooling;
the lubricating valve is opened when the oil pressure of the clutch control oil path is higher than or equal to a pressure threshold value, lubricating oil is provided for the clutch for cooling, and the lubricating valve is closed when the oil pressure is lower than the pressure threshold value.
Optionally, the friction work comprises accumulated friction work, and the accumulated friction work is used for describing a difference value between actual friction work and friction work counteracted by cooling and lubricating in unit time;
the clutch cooling and lubricating oil path further comprises: a first temperature sensor and a flow sensor disposed at an oil inlet of the lubrication valve, a second temperature sensor disposed at an oil outlet of the lubrication valve;
the first temperature sensor and the second temperature sensor are used for providing oil temperature for the controller;
the flow sensor is used for collecting the oil flow of the clutch cooling lubricating oil path and sending the oil flow to the controller;
the controller is specifically configured to determine the accumulated friction work according to the oil temperature and the oil flow.
Optionally, the clutch cooling lubricating oil path further includes: and the lubricating pump pressure limiting valve is used for returning the redundant oil quantity to the oil supply device when the oil quantity of the cooling lubricating oil circuit is higher than the specified oil quantity.
Optionally, the oil supply device includes: the oil tank, the oil tank check valve and the suction filter;
the oil tank is used for containing oil;
the oil tank one-way valve provides oil for the clutch control oil way and the clutch cooling and lubricating oil way;
and the suction filter is used for filtering the oil liquid which flows back to the oil tank.
Optionally, the system pump in the clutch control oil circuit and the lubrication pump in the clutch cooling lubrication oil circuit are driven by the engine.
Optionally, the controller is further configured to, when the clutch is in the engaged state, perform a protection operation on the clutch if a speed difference between rotation speeds of a driving disc and a driven disc of the clutch exceeds a protection limit value.
In a second aspect, the present application provides a hydro-mechanical cvt-based wet clutch protection method, the method comprising:
determining friction work of a clutch in the hydro-mechanical continuously variable transmission-based wet clutch protection system according to any one of the first aspect when the clutch is in a gear shifting state;
when the friction work of the clutch exceeds a corresponding threshold, a clutch protection measure is activated.
Optionally, the friction work includes an actual friction work in a unit time, and determining the actual friction work includes:
acquiring a speed difference between the rotating speeds of a driving disc and a driven disc of the clutch;
determining the product of the pressure value of the oil of the speed difference clutch control oil path and the clutch torque coefficient to obtain friction work power;
multiplying the friction work power by unit time to obtain the actual friction work;
when the friction work of the clutch exceeds a corresponding threshold, the clutch protection measures are started, and the method comprises the following steps:
and when the actual friction work is higher than the first friction work threshold, limiting the clutch to be lifted from the current gear to a gear higher than the current gear.
Optionally, the friction work comprises accumulated friction work, the accumulated friction work is used for describing a difference value between actual friction work and friction work offset by cooling and lubricating in unit time, and determining the accumulated friction work comprises:
collecting the temperature difference before and after the clutch is lubricated and cooled, and collecting the oil flow of a clutch cooling and lubricating oil way;
determining cooling power per unit time based on the temperature difference and the oil flow;
accumulating the difference between the actual friction work power and the cooling power in unit time to obtain the accumulated friction work;
when the friction work of the clutch exceeds a corresponding threshold, the clutch protection measures are started, and the method comprises the following steps:
and when the accumulated friction work is higher than the second friction work threshold, limiting the clutch to be lifted from the current gear to a gear higher than the current gear.
Optionally, the method further includes:
when the clutch is in a combined state, if the speed difference between the rotating speeds of the driving disk and the driven disk of the clutch exceeds a protection limit value, the protection operation of the clutch is executed.
The technical scheme provided by the embodiment of the application at least has the following beneficial effects:
carry out cooling and lubrication to the clutch under clutch shift state and combination state in this application, and do not carry out cooling and lubrication to it when the clutch is in the disengagement state, can guarantee to carry out cooling and lubrication as required from this, only play the effect when the gear shift process is with the state of shelves promptly, effectively improved the efficiency of cooling and lubrication oil circuit. In addition, in the embodiment of the application, when the gear shifting state is carried out, the controller can analyze the friction work, and when the friction work of the clutch exceeds a corresponding threshold, the clutch protection measure is started, so that when the heat generated by the sliding friction far exceeds the cooling lubricating system, the wear failure or ablation of the clutch can be avoided as far as possible, and the safety performance of the equipment is improved.
It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the disclosure.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings needed to be used in the embodiments of the present application will be briefly described below, and it is obvious that the drawings described below are only some embodiments of the present application, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.
Fig. 1 is a schematic structural diagram of a wet clutch protection system for a hydromechanical continuously variable transmission provided in an embodiment of the present application;
FIG. 2 is another schematic structural diagram of a wet clutch protection system for a hydromechanical continuously variable transmission provided by an embodiment of the present application;
FIG. 3 is a schematic flow chart illustrating a method for protecting a wet clutch of a hydromechanical continuously variable transmission according to an embodiment of the present disclosure;
FIG. 4 is another schematic flow chart illustrating a method for protecting a wet clutch of a hydromechanical continuously variable transmission according to an embodiment of the present disclosure;
FIG. 5 is a schematic structural diagram of a wet clutch protection device for a hydromechanical continuously variable transmission provided by an embodiment of the present application;
reference numerals: the system comprises an oil tank 1, an oil tank one-way valve 2, a suction filter 3, an engine 4, a system pump 5, a lubrication pump 6, a lubrication pump pressure limiting valve 7, an electromagnetic proportional valve 8, a cooler 9, a temperature control valve 10, a pressure sensor 11, a flow sensor 12, a temperature sensor 13, a lubrication valve 14, a clutch control oil cylinder 15, an oil supply device 101, a clutch control oil circuit 102, a clutch cooling lubrication oil circuit 103 and a controller 104.
Detailed Description
In order to make the technical solutions of the present application better understood by those of ordinary skill in the art, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings.
It should be noted that the terms "first," "second," and the like in the description and claims of this application 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 application described herein are capable of operation in sequences other than those illustrated or described herein. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with the present application. Rather, they are merely examples of apparatus and methods consistent with certain aspects of the present application, as detailed in the appended claims.
Hereinafter, some terms in the embodiments of the present application are explained to facilitate understanding by those skilled in the art.
(1) In the embodiments of the present application, the term "plurality" means two or more, and other terms are similar thereto.
(2) "and/or" describes the association relationship of the associated objects, meaning that there may be three relationships, e.g., a and/or B, which may mean: a exists alone, A and B exist simultaneously, and B exists alone. The character "/" generally indicates that the former and latter associated objects are in an "or" relationship.
(3) Sliding and grinding the clutch: when the clutch transmits torque, if the driving disk and the driven disk have speed difference, the relative motion between the driving disk and the driven disk causes the phenomenon that the clutch rotates and grinds.
(4) Friction work of the clutch: the heat generated when the clutch is worn. In the embodiment of the present application, the friction work includes actual friction work and accumulated friction work. The actual work of friction is used to describe the amount of heat generated by the slip film per unit time, and the cumulative work of friction is used to count the actual work of friction generated over a specified period of time minus the remaining work of friction offset by the cooling lubrication.
The prior art protects the sliding wear condition of the clutch under different working conditions by increasing the cooling and lubricating flow, the method is effective for vehicles with stable working conditions, but for equipment which often operates under the condition of complex environment and variable working conditions, when the equipment encounters a severe operating environment, a large external operating load can cause the clutch of the gearbox to generate severe sliding wear, the heat generated by the sliding wear far exceeds the protection capability of a cooling and lubricating system, the clutch is not protected by increasing the cooling and lubricating flow, and even the abrasion failure or ablation of the clutch is caused in severe conditions, so that the safe running of the equipment is influenced.
In view of this, the present embodiment provides a wet clutch protection system for a hydraulic mechanical continuously variable transmission, which includes an oil supply device 101, a clutch control oil path 102, a clutch cooling and lubricating oil path 103, and a controller 104, as shown in fig. 1, wherein:
the oil supply device 101 is configured to supply oil to the clutch control oil passage 102 and the clutch cooling and lubricating oil passage 103;
the clutch control oil path 102 is used for controlling oil to enter a clutch control oil cylinder (not shown in fig. 1) and controlling the clutch cooling and lubricating oil path 103 to cool and lubricate the clutch when the clutch is in a gear shifting state; when the clutch is in a separation state, controlling the clutch cooling and lubricating oil path 103 to stop cooling and lubricating the clutch;
the clutch cooling and lubricating oil path 103 is also used for continuously providing lubricating oil to cool and lubricate the clutch in the clutch combining process;
the controller 104 is configured to determine a work of friction of the clutch when the clutch is in the shift state, and to initiate a clutch protection measure when the work of friction of the clutch exceeds a corresponding threshold.
Therefore, in the embodiment of the application, the clutch control oil path 102 and the clutch cooling and lubricating oil path 103 are matched with each other, the clutch is cooled and lubricated in the clutch shifting state and the clutch combining state, and the clutch is not cooled and lubricated in the clutch separating state, so that cooling and lubricating can be ensured as required, namely, the clutch cooling and lubricating oil path only plays a role in the shifting process and the shifting state, and the efficiency of the cooling and lubricating oil path is effectively improved. In addition, in this embodiment of the application, during a gear shifting state, the controller 104 may analyze the friction work, and when the friction work of the clutch exceeds a corresponding threshold, a clutch protection measure is activated, so that when the heat generated by the slip wear far exceeds the cooling lubricating system, the wear failure or ablation of the clutch may be avoided as much as possible, and the safety performance of the device may be improved.
In one embodiment, a schematic structural view of the device portion of the clutch control oil path 102 is provided as shown in fig. 2. As shown in fig. 2, the clutch control oil passage 102 includes: the system comprises a system pump 5, an electromagnetic proportional valve 8 and a clutch control oil cylinder 15, wherein when the clutch enters a gear shifting state, the electromagnetic proportional valve 8 is electrified, and a valve core of the electromagnetic proportional valve 8 is gradually opened until the valve core reaches the maximum opening degree; the system pump 5 controls oil to enter the clutch control oil cylinder 15 through the electromagnetic proportional valve 8, so that the clutch combination is controlled.
Thus, the clutch control oil passage 102 can be immediately opened by the electromagnetic proportional valve 8 to control the clutch engagement.
In some embodiments, the work of friction comprises the actual work of friction per unit time, as previously described. As shown in fig. 2, the clutch control oil path 102 further includes: and the pressure sensor 11 is arranged between the electromagnetic proportional valve 8 and the clutch control oil cylinder 15 and is used for providing a pressure value to the controller 104. The controller 104 is thus configured to determine the actual friction work in particular from the pressure value and the time unit.
In one embodiment, the clutch has speed sensors mounted on both the driving and driven discs, such that the controller 104 can obtain the speed difference between the speeds of the driving and driven discs (i.e., the difference between the speeds of the driving and driven discs). Then, the controller 104 may determine the speed difference and the product between the pressure value of the oil in the clutch control oil path 102 and the clutch torque coefficient to obtain the friction work power, which is calculated as shown in equation (1):
P_FrictionClt＝trq_Clt*nDlt_Clt＝p_Clt*kTrq_Clt*nDlt_Clt (1)
in formula (1), P _ FrictionClt is clutch friction power; trq _ Clt is clutch transfer torque; nDlt _ Clt is the speed difference between the driving disk and the driven disk of the clutch; p _ Clt is clutch control pressure, namely a pressure value acquired by a pressure sensor 11 arranged between the electromagnetic proportional valve 8 and the control oil cylinder; kTrq _ Clt is the clutch torque coefficient.
After the friction power is obtained, the actual friction power is obtained by multiplying the friction power by the unit time. Then, the controller 104 may determine the actual friction work and the first friction work threshold, and when the actual friction work is higher than the first friction work threshold, the clutch is restricted from being lifted from the current gear to a gear higher than the current gear, so as to protect the clutch.
In the embodiment of the present application, the control of the clutch cooling lubricating oil passage 103 by the clutch control oil passage 102 may be implemented by the oil pressure of the clutch control oil cylinder 15. The device portion of the clutch cooling lubricating oil passage 103 is shown in fig. 2.
As shown in fig. 2, the clutch cooling lubricating oil passage 103 includes a lubricating pump 6, a cooler 9, a thermo valve 10, and a lubricating valve 14, and the oil supplied to the clutch cooling lubricating oil passage 103 includes a first branch oil and a second branch oil, wherein:
when the oil temperature is lower than the temperature threshold value, the temperature control valve 10 is closed, the oil liquid of the first branch flows to the lubricating valve through the cooler 9, and the oil liquid of the second branch bypasses the cooler 9 and flows to the lubricating valve; the temperature control valve 10 is closed, only a small part of oil passes through the cooler, and most of the oil directly flows to the lubricating valve from the branch without the cooler;
when the oil temperature is higher than or equal to the temperature threshold value, the temperature control valve 10 is opened, and all the oil in the first branch and the oil in the second branch flow to the lubricating valve after being cooled by the cooler 9;
the lubrication valve is opened when the oil pressure of the clutch control oil path 102 is higher than or equal to a pressure threshold value, supplies lubricating oil to the clutch for cooling, and is closed when the oil pressure is lower than the pressure threshold value.
To sum up, after the electromagnetic proportional valve 8 is powered on, namely after the clutch control oil path 102 supplies oil, the oil is input into the clutch control oil cylinder 15, in the clutch combination process, the lubricating valve 14 is also opened under the pressure action of the control oil, the lubricating oil provided by the lubricating pump 6 enters the clutch, and the clutch friction plate is cooled and lubricated; after the clutch is combined, the lubricating pump 6 continuously provides lubricating oil to cool and lubricate the clutch.
When the clutch is in a separation state, the electromagnetic valve is not electrified, the lubricating valve 14 is not opened by control oil, and the clutch is not cooled and lubricated by the cooling and lubricating oil circuit.
In addition to the actual frictional work described above, the frictional work in the embodiment of the present application may further include accumulated frictional work describing an accumulated result of a difference between the actual frictional work and the frictional work cancelled by the cooling lubrication.
In order to realize the statistics of the accumulated friction work, in the embodiment of the present application, as shown in fig. 2, the clutch cooling and lubricating oil path 103 further includes: a first temperature sensor 13 and a flow sensor 12 arranged at the oil inlet of the lubrication valve, a second temperature sensor 13 arranged at the oil outlet of the lubrication valve;
the first temperature sensor 13 and the second temperature sensor 13 are used for providing the oil temperature to the controller 104;
the flow sensor 12 is used for acquiring the oil flow of the clutch cooling and lubricating oil path 103 and sending the oil flow to the controller 104;
the controller 104 is specifically configured to determine the accumulated friction work according to the oil temperature and the oil flow.
In implementation, the controller 104 may collect the temperature difference before and after the clutch is lubricated and cooled, and collect the oil flow of the clutch cooling and lubricating oil path 103; then determining the cooling power in unit time based on the temperature difference and the oil liquid flow; and accumulating the difference between the actual friction work power and the cooling power in unit time to obtain the accumulated friction work.
The calculation formula of the accumulated frictional work may be implemented as: the clutch cooling power is first calculated in the manner shown in equation (2):
P_CoolingClt＝(T_OutClt-T_InClt)*Q_CoolingClt (2)
in equation (2), P _ coolnclt is the clutch cooling power; t _ OutClt is the clutch cooling outlet oil temperature (i.e., the temperature collected by the second temperature sensor 13); t _ InClt is the clutch cooling inlet oil temperature (i.e., the temperature collected by the first temperature sensor 13); q _ coolnclt is the clutch cooling flow (i.e., the oil flow collected by the flow sensor 12).
After the clutch cooling power is obtained, the cumulative friction work can be obtained as shown in equation (3):
W_CltSum＝∑((P_FrictionClt-P_CoolingClt)*ΔT) (3)
in equation (3), P _ FrictionClt represents clutch friction power, P _ coolnclt represents clutch cooling power, and Δ T represents unit time.
Therefore, after the accumulated friction work is obtained, the accumulated friction work can be compared with a corresponding second friction work threshold, and when the accumulated friction work is higher than the second friction work threshold, the clutch is limited from being lifted from the current gear to a gear higher than the current gear, so that the clutch is protected.
In another embodiment, the controller 104 may not only protect the shift state but also protect the engaged state of the clutch, such as when the clutch is in the engaged state, if the speed difference between the rotation speeds of the driving plate and the driven plate of the clutch exceeds a protection limit, then a protection operation of the clutch is performed, such as limiting the entering of a high gear.
In the embodiment of the present application, in order to facilitate control over the clutch control oil path 102 and the clutch cooling lubrication oil path 103, as shown in fig. 2, the system pump 5 in the clutch control oil path 102 and the lubrication pump 6 in the clutch cooling lubrication oil path 103 are driven by the engine 4.
In another embodiment, in order to avoid providing too much oil to cool the clutch, in this embodiment, as shown in fig. 2, the clutch cooling and lubricating oil path 103 further includes: and the lubricating pump pressure limiting valve 7 is used for returning the surplus oil quantity to the oil supply device 101 when the oil quantity of the cooling lubricating oil circuit is higher than the specified oil quantity.
Accordingly, in another embodiment, as shown in fig. 2, the oil supply device 101 includes: the oil tank comprises an oil tank 1, an oil tank one-way valve 2 and a suction filter 3;
the oil tank 1 is used for containing oil;
the oil tank one-way valve 2 is used for providing oil to the clutch control oil path 102 and the clutch cooling lubricating oil path 103;
and the suction filter 3 is used for filtering the oil liquid which flows back to the oil tank 1.
Thus, the check valve can feed the oil to the clutch control oil passage 102 and the clutch cooling/lubricating oil passage 103 in one direction, and the suction filter 3 can filter the amount of the returned oil.
Based on the same inventive concept, the embodiment of the present application further provides a method for protecting a wet clutch based on a hydraulic mechanical continuously variable transmission, as shown in fig. 3, which is a schematic flow chart of the method, and includes the following steps:
in step 301, determining friction work based on a clutch in a wet clutch protection system of a hydro-mechanical continuously variable transmission when the clutch is in a gear shifting state;
in step 302, clutch protection measures are activated when the friction work of the clutch exceeds a corresponding threshold.
Optionally, the friction work includes an actual friction work in a unit time, and determining the actual friction work includes:
acquiring a speed difference between the rotating speeds of a driving disc and a driven disc of the clutch;
determining the product of the pressure value of the oil of the clutch control oil path 102 and the clutch torque coefficient to obtain friction work power;
multiplying the friction work power by unit time to obtain the actual friction work;
when the friction work of the clutch exceeds a corresponding threshold, the clutch protection measures are started, and the method comprises the following steps:
and when the actual friction work is higher than the first friction work threshold, limiting the clutch to be lifted from the current gear to a gear higher than the current gear.
Optionally, the friction work comprises accumulated friction work, the accumulated friction work is used for describing a difference value between actual friction work and friction work offset by cooling and lubricating in unit time, and determining the accumulated friction work comprises:
collecting the temperature difference before and after the clutch is lubricated and cooled, and collecting the oil flow of a clutch cooling and lubricating oil path 103;
determining cooling power per unit time based on the temperature difference and the oil flow;
accumulating the difference between the actual friction work power and the cooling power in unit time to obtain the accumulated friction work;
when the friction work of the clutch exceeds a corresponding threshold, the clutch protection measures are started, and the method comprises the following steps:
and when the accumulated friction work is higher than the second friction work threshold, limiting the clutch to be lifted from the current gear to a gear higher than the current gear.
Optionally, the method further includes:
when the clutch is in a combined state, if the speed difference between the rotating speeds of the driving disk and the driven disk of the clutch exceeds a protection limit value, the protection operation of the clutch is executed.
For ease of understanding, the protection method is further described below with reference to fig. 2:
the friction work generated by the sliding wear in the clutch combination process is prevented from exceeding the limit, the clutch ablation condition caused by the protective capacity of a far-exceeding cooling lubricating system is prevented from occurring, and the condition that the clutch friction plate is abraded and aggravated due to the fact that the clutch speed difference exceeds the limit caused by large transmission torque in the clutch combination state is prevented from occurring.
As shown in fig. 4, in step 401, clutch friction power is calculated based on clutch torque and clutch speed difference when the clutch is in a shift state.
The clutch transmission torque is calculated by a clutch control pressure and a torque coefficient, the clutch control pressure is measured by a pressure sensor 1111 in fig. 1, the clutch speed difference is measured by a rotation speed sensor on the driving disk side and the driven disk side of the clutch, the rotation speed sensor is not shown in fig. 2, and the calculation formula of the clutch friction power is as shown in formula (1):
P_FrictionClt＝trq_Clt*nDlt_Clt＝p_Clt*kTrq_Clt*nDlt_Clt (1)
wherein P _ FrititionClt is clutch friction power; trq _ Clt is clutch transfer torque; nDlt _ Clt is the speed difference between the driving disk and the driven disk of the clutch; p _ Clt is clutch control pressure, namely a pressure value acquired by a pressure sensor 11 arranged between the electromagnetic proportional valve 8 and the control oil cylinder; kTrq _ Clt is the clutch torque coefficient.
In step 402, clutch cooling power is calculated according to the temperature difference between the inlet and outlet of the clutch cooling lubricant and the cooling lubricant flow.
The inlet-outlet temperature is measured by an inlet-outlet temperature sensor 1313 in fig. 2, the cooling and lubricating flow is measured by a flow sensor 1212 in fig. 2, and the clutch cooling power calculation formula (2) is:
P_CoolingClt＝(T_OutClt-T_InClt)*Q_CoolingClt； (2)
in equation (2), P _ coolnclt is the clutch cooling power; t _ OutClt is the clutch cooling outlet oil temperature (i.e., the temperature collected by the second temperature sensor 13); t _ InClt is the clutch cooling inlet oil temperature (i.e., the temperature collected by the first temperature sensor 13); q _ coolnclt is the clutch cooling flow (i.e., the oil flow collected by the flow sensor 12).
In step 403, the actual friction work of the clutch is calculated according to the calculated clutch friction power, and the calculation formula (4) of the actual friction work of the clutch is as follows:
w _ CltAct ═ Σ (P _ FrictionClt Δ T), where Δ T is the time of one step, i.e., the unit time described above, and W _ CltAct is the actual work of friction.
In step 404, a clutch accumulated friction work is calculated based on the calculated clutch friction power and clutch cooling power, and the clutch accumulated friction work calculation formula (3) is:
W_CltSum＝∑(P_FrictionClt-P_CoolingClt)*ΔT； (3)
in equation (3), P _ FrictionClt represents clutch friction power, P _ coolnclt represents clutch cooling power, and Δ T represents unit time.
In step 405, it is determined whether the calculated clutch actual friction work and the clutch accumulated friction work exceed the respective protection limits.
In step 406, clutch protection is enabled as long as one of them exceeds a limit, limiting the clutch from going into high range, and no limitation is made if the limit is not exceeded.
In step 407, when the clutch is in the engaged state, it is determined whether the clutch speed difference exceeds a protection limit, if so, all gears are limited, and if not, no limitation is made; when the clutch is in the disengaged state, no limitation is imposed.
The maximum transmission ratio of the hydraulic mechanical stepless gearbox is determined according to the clutch protection limit obtained by judging the conditions, so that the combination of the clutch is limited, and the aims of preventing the clutch from being abraded and being ablated due to heat generated by sliding abrasion are fulfilled.
Based on the same inventive concept, the embodiment of the present application further provides a wet clutch protection device based on a hydro-mechanical continuously variable transmission, as shown in fig. 5, the device 500 includes:
the friction work determining module 501 is configured to determine friction work of a clutch in any one of the hydraulic mechanical continuously variable transmission-based wet clutch protection systems when the clutch is in a shift state;
a protection module 502 activates clutch protection measures when a friction work of a clutch exceeds a corresponding threshold.
Optionally, the friction work includes an actual friction work in a unit time, the actual friction work is determined, and the friction work determining module 501 is specifically configured to:
acquiring a speed difference between the rotating speeds of a driving disc and a driven disc of the clutch;
determining the product of the pressure value of the oil of the speed difference clutch control oil path and the clutch torque coefficient to obtain friction work power;
multiplying the friction work power by unit time to obtain the actual friction work;
the protection module 502 is specifically configured to:
and when the actual friction work is higher than the first friction work threshold, limiting the clutch to be lifted from the current gear to a gear higher than the current gear.
Optionally, the friction work includes an accumulated friction work, the accumulated friction work is used to describe a difference between an actual friction work and a friction work offset by cooling and lubricating in a unit time, and the friction work determining module 501 is specifically configured to:
collecting the temperature difference before and after the clutch is lubricated and cooled, and collecting the oil flow of a clutch cooling and lubricating oil way;
determining cooling power per unit time based on the temperature difference and the oil flow;
accumulating the difference between the actual friction work power and the cooling power in unit time to obtain the accumulated friction work;
the protection module 502 is specifically configured to:
and when the accumulated friction work is higher than the second friction work threshold, limiting the clutch to be lifted from the current gear to a gear higher than the current gear.
Optionally, the protection module 502 is further configured to:
when the clutch is in a combined state, if the speed difference between the rotating speeds of the driving disk and the driven disk of the clutch exceeds a protection limit value, the protection operation of the clutch is executed.
As will be appreciated by one skilled in the art, embodiments of the present application may be provided as a method, system, or computer program product. Accordingly, the present application may take the form of an entirely hardware embodiment, an entirely software embodiment or an embodiment combining software and hardware aspects. Furthermore, the present application may take the form of a computer program product embodied on one or more computer-usable storage media (including, but not limited to, disk storage, CD-ROM, optical storage, and the like) having computer-usable program code embodied therein.
The present application is described with reference to flowchart illustrations and/or block diagrams of methods, apparatus (systems), and computer program products according to the application. It will be understood that each flow and/or block of the flow diagrams and/or block diagrams, and combinations of flows and/or blocks in the flow diagrams and/or block diagrams, can be implemented by computer program instructions. These computer program instructions may be provided to a processor of a general purpose computer, special purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, create means for implementing the functions specified in the flowchart flow or flows and/or block diagram block or blocks.
These computer program instructions may also be stored in a computer-readable memory that can direct a computer or other programmable data processing apparatus to function in a particular manner, such that the instructions stored in the computer-readable memory produce an article of manufacture including instruction means which implement the function specified in the flowchart flow or flows and/or block diagram block or blocks.
These computer program instructions may also be loaded onto a computer or other programmable data processing apparatus to cause a series of operational steps to be performed on the computer or other programmable apparatus to produce a computer implemented process such that the instructions which execute on the computer or other programmable apparatus provide steps for implementing the functions specified in the flowchart flow or flows and/or block diagram block or blocks.
It will be apparent to those skilled in the art that various changes and modifications may be made in the present application without departing from the spirit and scope of the application. Thus, if such modifications and variations of the present application fall within the scope of the claims of the present application and their equivalents, the present application is intended to include such modifications and variations as well.
Claims (13)
1. The utility model provides a wet clutch protection system based on hydraulic pressure machinery buncher, its characterized in that includes oil supply unit, clutch control oil circuit and clutch cooling lubrication oil circuit and controller, wherein:
the oil supply device is used for supplying oil to the clutch control oil way and the clutch cooling and lubricating oil way;
the clutch control oil way is used for controlling oil to enter the clutch control oil cylinder when the clutch is in a gear shifting state and controlling the clutch cooling and lubricating oil way to cool and lubricate the clutch; when the clutch is in a separation state, controlling the clutch cooling and lubricating oil path to stop cooling and lubricating the clutch;
the clutch cooling lubricating oil path is also used for continuously providing lubricating oil to cool and lubricate the clutch in the combining process of the clutch;
the controller is used for determining the friction work of the clutch when the clutch is in a gear shifting state, and starting a clutch protection measure when the friction work of the clutch exceeds a corresponding threshold.
2. The system of claim 1, wherein the clutch control circuit comprises: system pump, electromagnetism proportional valve and clutch control hydro-cylinder, wherein:
when the clutch enters a gear shifting state, the electromagnetic proportional valve is electrified, and the valve core of the electromagnetic valve is gradually opened until the valve core reaches the maximum opening degree;
and the system pump controls oil to enter the clutch control oil cylinder through the electromagnetic proportional valve to control the clutch to be combined.
3. The system of claim 2, wherein the work of friction comprises actual work of friction per unit time;
the clutch control oil passage further includes: the pressure sensor is arranged between the electromagnetic proportional valve and the control oil cylinder and used for providing a pressure value for the controller;
the controller is specifically configured to determine the actual friction work according to the pressure value and the unit time.
4. The system of claim 1, wherein the clutch cooling lube circuit includes a lube pump, a cooler, a thermostatic valve, and a lube valve, and the oil provided to the clutch cooling lube circuit includes a first branch of oil and a second branch of oil, wherein:
when the oil temperature is lower than the temperature threshold value, the temperature control valve is closed, the oil liquid of the first branch flows to the lubricating valve through the cooler, and the oil liquid of the second branch bypasses the cooler and flows to the lubricating valve;
when the oil temperature is higher than or equal to a temperature threshold value, the temperature control valve is opened, and all the oil in the first branch and the oil in the second branch flow to the lubricating valve after flowing through the cooler for cooling;
the lubricating valve is opened when the oil pressure of the clutch control oil path is higher than or equal to a pressure threshold value, lubricating oil is provided for the clutch for cooling, and the lubricating valve is closed when the oil pressure is lower than the pressure threshold value.
5. The system of claim 4, wherein the work of friction comprises an accumulated work of friction describing a difference between actual work of friction and work of friction offset by cooling lubrication per unit time;
the clutch cooling and lubricating oil path further comprises: a first temperature sensor and a flow sensor disposed at an oil inlet of the lubrication valve, a second temperature sensor disposed at an oil outlet of the lubrication valve;
the first temperature sensor and the second temperature sensor are used for providing oil temperature for the controller;
the flow sensor is used for collecting the oil flow of the clutch cooling lubricating oil path and sending the oil flow to the controller;
the controller is specifically configured to determine the accumulated friction work according to the oil temperature and the oil flow.
6. The system of claim 4, wherein the clutch cooling lubrication circuit further comprises: and the lubricating pump pressure limiting valve is used for returning the redundant oil quantity to the oil supply device when the oil quantity of the cooling lubricating oil circuit is higher than the specified oil quantity.
7. The system according to any one of claims 1 to 6, wherein the oil supply device comprises: the oil tank, the oil tank check valve and the suction filter;
the oil tank is used for containing oil;
the oil tank one-way valve provides oil for the clutch control oil way and the clutch cooling and lubricating oil way;
and the suction filter is used for filtering the oil liquid which flows back to the oil tank.
8. The system of claim 2 or 4, wherein a system pump in the clutch control oil circuit and a lubrication pump in the clutch cooling lubrication oil circuit are driven by the engine.
9. The system of any of claims 1-6, wherein the controller is further configured to perform a protective operation on the clutch if a speed differential between rotational speeds of a driving plate and a driven plate of the clutch exceeds a protective limit while the clutch is in the engaged state.
10. A hydro-mechanical Continuously Variable Transmission (CVT) based wet clutch protection method is characterized by comprising the following steps:
determining the friction work of the clutch in the hydro-mechanical continuously variable transmission based wet clutch protection system according to any one of claims 1-9 when the clutch is in a gear shifting state;
when the friction work of the clutch exceeds a corresponding threshold, a clutch protection measure is activated.
11. The method of claim 10, wherein the work of friction comprises actual work of friction per unit time, and wherein determining the actual work of friction comprises:
acquiring a speed difference between the rotating speeds of a driving disc and a driven disc of the clutch;
determining the product of the pressure value of the oil of the speed difference clutch control oil path and the clutch torque coefficient to obtain friction work power;
multiplying the friction work power by unit time to obtain the actual friction work;
when the friction work of the clutch exceeds a corresponding threshold, the clutch protection measures are started, and the method comprises the following steps:
and when the actual friction work is higher than the first friction work threshold, limiting the clutch to be lifted from the current gear to a gear higher than the current gear.
12. The method of claim 10, wherein the work of friction comprises an accumulated work of friction describing a difference between actual work of friction and work of friction offset by cooling lubrication per unit time, and wherein determining the accumulated work of friction comprises:
collecting the temperature difference before and after the clutch is lubricated and cooled, and collecting the oil flow of a clutch cooling and lubricating oil way;
determining cooling power per unit time based on the temperature difference and the oil flow;
accumulating the difference between the actual friction work power and the cooling power in unit time to obtain the accumulated friction work;
when the friction work of the clutch exceeds a corresponding threshold, the clutch protection measures are started, and the method comprises the following steps:
and when the accumulated friction work is higher than the second friction work threshold, limiting the clutch to be lifted from the current gear to a gear higher than the current gear.
13. The method according to any one of claims 10-12, further comprising:
when the clutch is in a combined state, if the speed difference between the rotating speeds of the driving disk and the driven disk of the clutch exceeds a protection limit value, the protection operation of the clutch is executed.
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