CN115859844B - Lubrication and cooling simulation method for wet clutch - Google Patents
Lubrication and cooling simulation method for wet clutch Download PDFInfo
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- CN115859844B CN115859844B CN202210902389.3A CN202210902389A CN115859844B CN 115859844 B CN115859844 B CN 115859844B CN 202210902389 A CN202210902389 A CN 202210902389A CN 115859844 B CN115859844 B CN 115859844B
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Abstract
The invention discloses a wet clutch lubrication cooling simulation method, which comprises the following steps: collecting motion data of the internal parts of the clutch in four motion stages of a sliding friction stage, a combining stage, a half-separating stage and a full-separating stage, and performing parameterization treatment, wherein the motion data comprise relative rotation speed, torque and friction force; inputting the rotating speed, torque and friction force of the internal parts of the clutch by using a temperature solver or a finite element analysis method, and obtaining curves of temperature changing along with time in four movement stages; obtaining the oil product characteristic change condition of clutch lubricating oil according to the temperature curve; the influence of external parts of the clutch on clutch oil is obtained through dynamic simulation, and a corresponding oil way is established; and constructing a clutch fluid dynamics model by using CAE software, and outputting an optimal design result on a CFD fluid dynamics software platform to obtain oil mass data and lubrication cooling conditions of important parts of the clutch. The invention has higher simulation precision and shortens the design period.
Description
Technical Field
The invention belongs to the technical field of fluid simulation of automobile power systems, and particularly relates to a lubrication and cooling simulation method for a wet clutch of an automobile gearbox.
Background
The conventional clutch lubrication simulation model generally adopts an equivalent model, and the clutch is independently separated from the gearbox for analysis. The advantage of this is that the structure is simpler and the calculation is faster for the whole gearbox; the method has the defects that the influence of the motion state of parts outside the clutch on oil throwing and oil return is not calculated, and the simulation oil way result is easily distorted by simply depending on the motion state of the clutch, so that inaccurate precision is caused.
The clutch lubrication and cooling simulation is carried out by adopting the method, the simulation calculation time is short and is about 2 seconds, and the constant temperature of about 90 ℃ is adopted when the simulation is carried out, which is not in accordance with the actual situation. Due to the specificity of the clutch, the friction effect of the friction plate can greatly improve the temperature instantly, and the oil product characteristics and the lubrication and cooling efficiency are affected. And the operating conditions of the clutch are different under the operating conditions of starting, constant speed, ascending slope, descending slope, passing over a rugged road surface and the like of the vehicle by combining the operating conditions of the whole vehicle, and the temperature change is also different, so that the oil product characteristics corresponding to the temperature are also different.
However, if the whole gearbox is integrally simulated, a plurality of factors need to be considered, and fig. 1 of the specification is a factor which affects the lubrication state of the clutch and is arranged by the inventor, for example, the internal parts of the clutch and the external parts related to the clutch have more or less influence on the lubrication state of the clutch. If the whole gearbox is subjected to integral simulation, the simulation takes a long time, more than one week is needed, and the development period is influenced. Therefore, it is needed to design a wet clutch lubrication cooling simulation method, which can more accurately and more efficiently simulate working conditions and obtain enough simulation data.
Disclosure of Invention
Aiming at the defects existing in the prior art, the invention aims to provide a novel automobile clutch lubrication cooling simulation method, which improves simulation precision and shortens design period.
In order to achieve the above object, the present invention provides a wet clutch lubrication cooling simulation method, comprising the steps of:
1. collecting motion data of the internal parts of the clutch in four motion stages of a sliding friction stage, a combination stage, a half-separation stage and a full-separation stage, and performing parameterization treatment, wherein the motion data comprise relative rotation speed, torque, friction coefficient and the like;
2. a temperature solver module analysis method or a finite element analysis method in multi-body dynamics simulation is adopted, and the rotation speed, torque, friction coefficient and the like of internal parts of the clutch are input to obtain curves of temperature change along with time in four movement stages;
3. according to the temperature curve, the oil product characteristic change condition of the clutch lubricating oil is obtained, and the change formula of the temperature and the dynamic viscosity and the volume viscosity of the lubricating oil is as follows:
lglg(v+C)＝A+mlgT
v is the viscosity of the oil product at the temperature T (273+t ℃) and the unit is mm2/s and A, C, m is a constant;
4. the influence of external parts of the clutch on clutch oil is obtained through dynamic simulation, and a corresponding oil way is established according to the following conditions: the oil throwing and splashing effects promote the increase or decrease of the oil quantity, change of the motion state of oil particles, influence of the rotating direction on positive pressure or negative pressure and influence on the oil return quantity of the clutch;
5. on the basis of the step 4, oil stirring simulation is carried out under the whole tank environment under a certain working condition through CFD fluid simulation software, and the statistics of variables such as the oil quantity, the speed and the position of lubricating oil produced by the clutch due to the motion effect of external parts of the clutch are counted, so that the parameters of the clutch are parameterized;
6. constructing a clutch fluid simulation model by using CFD fluid simulation software, inputting different oil product characteristic curves of the clutch, which are obtained in the step 3 and are affected by temperature, in each stage, on the one hand, and on the other hand, according to the influence of external parts of the clutch on the oil quantity, speed and the like of the clutch in the step 5, establishing oil sources at corresponding positions under the same working condition, and spraying the oil sources to the clutch in a parameterized mode, namely, the effect of once and for all, so that the improvement of efficiency, accuracy and precision under the same working condition can be achieved;
7. and (3) analyzing and evaluating whether the calculation result meets the expected design index, when the calculation result does not meet the expected design index, carrying out optimal design on related components of the cooling system, and re-executing the steps S1-S5, and when the calculation result meets the expected design index, outputting the optimal design result to obtain oil mass data and lubrication cooling conditions of important parts focused by the clutch.
In the step S1, the clutch internal parts comprise a return spring group, a friction plate, a pair of plates, a balance plate, a piston, a bearing, an inner bracket, a driven gear and an intermediate shaft.
Further, in step S4, the clutch external part parameters include the rotational speed and direction of the engine tooth shaft and the differential tooth shaft.
Further, in step S5, the mesh of the following portions is refined: the inner and outer bracket holes, the friction plate pair gap, the intermediate shaft oil hole, the balance plate and the gap between the shafts.
Further, in the step S5, parameters of oil product characteristics in four stages include temperature, dynamic viscosity, volume viscosity, tension coefficient and density.
The invention has the beneficial effects that:
compared with the traditional clutch lubrication cooling simulation method, the wet clutch lubrication cooling simulation method disclosed by the invention has the advantages that the simulation precision is higher, the actual state is more fitted, the calculation efficiency is improved, and the design period is greatly shortened.
Drawings
FIG. 1 is a schematic diagram of a hydraulic control system employing a pressure limiting valve for back flow as described in the background art;
FIG. 2 is a graph showing the temperature and viscosity of the present invention at four motion stages;
FIG. 3 is a schematic illustration of a clutch according to the present invention subjected to external oil slinging or return action;
FIG. 4 is a schematic illustration of the amount of oil splatter over time for a clutch outer according to the present invention;
FIG. 5 is a graph showing average values of splash oil quantity of three holes of the balance sheet according to the invention over time;
FIG. 6 is a graph showing average values of oil splashing amount of friction plates according to the present invention over time;
FIG. 7 is a graph showing the average value of the splash oil quantity of the waist-shaped hole of the inner bracket according to the invention as a function of time;
FIG. 8 is a graph showing average values of splash oil quantity of a central hole of an intermediate shaft of an engine according to the invention over time;
FIG. 9 is a graph showing average values of splash oil quantity over time for a lower bore of an engine intermediate shaft according to the present invention;
FIG. 10 is a graph showing average values of splash oil quantity of a middle hole of an intermediate shaft of an engine according to the present invention over time;
fig. 11 is a schematic step diagram of a wet clutch lubrication cooling simulation method according to the present invention.
Detailed Description
The preferred embodiments of the present invention will be described below with reference to the accompanying drawings, it being understood that the preferred embodiments described herein are for illustration and explanation of the present invention only, and are not intended to limit the present invention.
As shown in fig. 1 and 11, a wet clutch lubrication cooling simulation method includes the following steps:
firstly, collecting motion data of the internal parts of the clutch in four motion stages of a sliding friction stage, a combining stage, a half-separating stage and a full-separating stage, and carrying out parameterization treatment, wherein the motion data comprise relative rotation speed, torque and friction force; the clutch inner part comprises a return spring group, a friction plate, a pair of plates, a balance plate, a piston, a bearing, an inner bracket, a driven gear and an intermediate shaft.
Secondly, inputting the rotating speed, torque and friction force of the internal parts of the clutch by adopting a temperature solver or a finite element analysis method, and obtaining curves of the temperature changing along with time in four movement stages;
thirdly, according to a temperature curve, obtaining the oil property change condition of clutch lubricating oil, wherein a change formula of temperature, dynamic viscosity and volume viscosity of the lubricating oil is as follows:
lglg(v+C)＝A+mlgT
v is the viscosity of the oil product at the temperature T (273+t ℃) and the unit is mm2/s and A, C, m is a constant;
fourthly, obtaining the influence of external parts of the clutch on clutch oil through dynamic simulation, and establishing a corresponding oil way according to the following conditions: the oil throwing and splashing effects promote the increase or decrease of the oil quantity, change of the motion state of oil particles, influence of positive pressure or negative pressure on the oil particles caused by the rotation direction and influence of oil return of a clutch on the oil quantity; the clutch external part parameters comprise the rotation speed and the direction of an engine gear shaft and a differential gear shaft. Carrying out oil stirring simulation under the whole box environment under a certain working condition by CFD fluid simulation software, and counting variables such as the oil quantity, the speed, the position and the like of lubricating oil generated by a clutch due to the motion effect of external parts of the clutch, so that the parameters of the clutch are parameterized;
and fifthly, constructing a clutch fluid simulation model by utilizing CFD fluid simulation software, on one hand, inputting different oil product characteristic curves of the clutch, which are obtained in the step 3 and are influenced by temperature, on the other hand, according to the influence of external parts of the clutch on the oil quantity, speed and the like of the clutch in the step 5, establishing oil sources at corresponding positions under the same working condition, and spraying the oil sources to the clutch in a parameterized mode, namely, the effect of once and for all, so that the improvement of efficiency, accuracy and precision under the same working condition can be achieved.
And step six, analyzing and evaluating whether the calculation result meets the expected design index, optimally designing the related components of the cooling system when the calculation result does not meet the expected design index, and re-executing the steps S1-S5, and outputting the optimal design result when the calculation result meets the expected design index to obtain the oil mass data and the lubrication cooling condition of the important parts of the clutch.
Constructing a clutch fluid dynamics model by CAE software, adopting a conventional CFD model modeling step on a CFD fluid dynamics software platform, replacing flow resistance characteristics of a friction plate, a dual plate and a balance plate by a universal resistance element, replacing actual lubrication characteristics by a rotating speed-flow-lift change curve, replacing an actual oil path structure by length, diameter and guide angle parameters, introducing an oil path formed by an oil product characteristic curve and an external part into the model, carrying out simulation calculation by combining boundary conditions, a sliding friction stage, a combining stage, a semi-separating stage and a full separating stage, filling relevant data after parameterization into parameter tables of corresponding parts in the CFD model, and solving a continuity equation, a momentum equation and an energy equation by iterative calculation, thereby constructing the dynamics model completely; the mesh of the following parts is refined: the inner and outer bracket holes, the friction plate pair gap, the intermediate shaft oil hole, the balance plate and the gap between the shafts. Parameters of the oil properties in four stages include temperature, dynamic viscosity, volumetric viscosity, tension coefficient, density.
And step six, analyzing and evaluating whether the calculation result meets the expected design index, optimally designing the related components of the cooling system when the calculation result does not meet the expected design index, and re-executing the steps S1-S5, and outputting the optimal design result when the calculation result meets the expected design index to obtain the oil mass data and the lubrication cooling condition of the important parts of the clutch.
The working principle of the invention is as follows:
the invention aims at two factors of an internal part and a clutch external part which are mentioned in the background, and starts from two directions, firstly, the motion state of the clutch is divided into four stages according to the working conditions of the whole vehicle: a sliding and rubbing stage, a combining stage, a semi-separation stage and a complete separation stage.
1. The sliding friction stage is that the friction plate and the dual plate have relative speed, are in a state before combination, have larger gap with oil liquid, have friction effect and enhance friction, and have quicker heating;
2. the combination stage is that the friction plate and the dual plate have no relative rotation speed, oil liquid only circulates from the toe base gap of the friction plate, no friction exists, and the temperature is unchanged;
3. the half-separation stage refers to a state that the friction plate and the dual plate have relative speeds after being combined, oil exists in a larger gap between the friction plate and the dual plate, the friction effect is reduced, and the temperature is slightly increased;
4. the complete separation state is that after the half separation state, the friction plate and the dual plate have relative speeds, the gap between the friction plate and the dual plate reaches the maximum value, the oil liquid is the most, and the temperature is reduced rapidly.
By temperature field or finite element simulation (more accurate), will
As shown in fig. 1 of the specification, according to the division of four stages, the model utilizes dynamic simulation analysis to obtain motion parameters under the four stages, including a relative rotation speed curve, a torque curve, a friction curve, a temperature curve and the like, and then influences the oil properties of the clutch lubricating oil according to the obtained curves (mainly, the temperature), for example: and fitting the dynamic viscosity, the volume viscosity, the tension coefficient, the density and the like to obtain the parameter curves of the oil products.
lglg(v+C)＝A+mlgT
v is the viscosity of the oil product at temperature T (273+t ℃) and mm2/s and A, C, m is a constant.
As shown in figure 2 of the specification, the temperature curve of a certain oil product in the four stages is shown in a schematic diagram.
The other direction starts from the motion influence of external parts of the clutch, and the influence of the rotation speed, the steering and the like of the engine gear shaft and the differential gear shaft on clutch oil liquid is obtained through dynamic simulation. Such as their oil slinging, splash effects causing an increase or decrease in the amount of oil, a change in the state of motion of the oil particles, an effect of the direction of rotation on either positive or negative pressure, an effect of clutch oil return, etc. Through the influence state of peripheral parts on the clutch, a corresponding oil way can be established in the clutch lubrication cooling simulation analysis model, so that the modeling of the whole gearbox is avoided, the independent modeling efficiency of the clutch is ensured, and the influence of other parts is covered. The precision is improved while the efficiency is ensured.
Fig. 3 is a schematic diagram of measures of throwing oil or returning oil from outside the clutch, which are made in consideration of the influence of the motion of external parts.
The parameters obtained by the dynamic simulation analysis in the two aspects are adopted, then the conventional CFD model modeling step is carried out, the grids of certain important parts are divided and processed, and the grids of certain important parts are refined (such as the number of the friction plate grids is not less than three, the number of the toe base grids is not less than three), and finally the CFD model is built, and the parameters (the oil product characteristic curve and the influence of external parts) are imported into the model, so that the oil quantity and the lubrication and cooling conditions of the important parts concerned by the clutch are obtained. Such as: the oil flow of the inner and outer bracket holes, the gap flow of the friction plate pair plates, the oil flow of the middle shaft oil hole, the gap oil flow between the balance plate and the shaft, and the like. Therefore, the simulation precision can be improved, the actual state can be attached more, and the calculation efficiency can be improved.
The working process of the invention (explained in one example):
boundary conditions: the vehicle-mounted angle of the transmission is 0 degree, the vehicle speed is 60km/h, the lubricating oil quantity of the transmission is 2.43L, and the working condition of sliding friction is as follows: the steel sheet and outer bracket rotate at 1762rpm, the friction sheet and inner bracket rotate at 1716rpm, simulate the lubrication condition of all parts in the clutch under the state. Compared with other stages, the sliding stage is more important because the temperature gradient is larger in the sliding stage and the characteristic parameters such as oil viscosity and the like are also larger in the sliding stage. This example therefore simulates only clutch slip phase lubrication conditions, as follows:
on the one hand: the motion state and the temperature change of the clutch are obtained through dynamic simulation. Kinematic simulation input parameters: establishing contact relation and kinematic pair between parts, and sliding and rubbing working conditions: the rotation speed of the steel sheet in the motion state of the part is 1762rpm, the rotation speed of the friction plate is 1716rpm, and the friction coefficient is 0.15. And outputting a temperature change curve.
The law of viscosity change is obtained by temperature change and the following temperature-viscosity equation:
lglg(v+C)＝A+mlgT
v is the viscosity of the oil product at temperature T (273+t ℃) and mm2/s and A, C, m is a constant.
On the other hand, the oil slinging effect of the parts outside the clutch is established. In the whole gearbox environment, the splash oil quantity of parts (such as engine shaft teeth and differential mechanism shaft teeth) outside the clutch on the clutch outer support is calculated as shown in the accompanying drawing 4 of the specification, an oil source plane is built in lubrication simulation software according to the flow curve of the accompanying drawing 4 per second, and the oil quantity is injected into the clutch outer support. The clutch is also applicable if the internal parts of the clutch are changed or adjusted under the same working condition of the gearbox.
4 steel sheets with the same rotation speed: 1762rpm,4 friction plates with same rotational speed: 1716rpm (rotational speed difference between friction plate and steel plate 46 rpm); calculating the time length: about 2S.
Fig. 5-9 are model results comparison for the pre-and post-optimization slip phase: the flow difference between the key parts before and after optimization is obvious between the model 1 (opt 1) after optimization and the model 2 (opt 2) before optimization, the invention considers the temperature and viscosity change of lubricating oil and the influence of a plurality of external components, and the simulation precision is higher.
Description figure 5 is the average flow rate of the three oil holes on the balancing piece over time;
description figure 6 is an average flow rate of friction plate gap over time;
description figure 7 is the average flow rate over time for a carrier web-shaped aperture in a clutch;
figures 8-10 of the accompanying drawings show the average flow rate of the engine center and side ports over time.
The foregoing has outlined and described the basic principles, features, and advantages of the present invention. It should be understood by those skilled in the art that the foregoing embodiments are merely illustrative of the technical concept and features of the present invention, and the present invention can be implemented by those skilled in the art without limiting the scope of the invention, therefore, all equivalent changes or modifications that are made according to the spirit of the present invention should be included in the scope of the present invention.
Claims (5)
1. A wet clutch lubrication cooling simulation method is characterized in that: the method comprises the following steps:
s1, collecting motion data of internal parts of a clutch in four motion stages of a sliding friction stage, a combination stage, a half-separation stage and a full-separation stage, and performing parameterization treatment, wherein the motion data comprise relative rotation speed, torque and friction coefficient;
s2, inputting parameters including rotation speed, torque and friction coefficient of internal parts of the clutch by adopting a temperature solver module analysis method or a finite element analysis method in multi-body dynamics simulation, and obtaining curves of temperature changing along with time in four movement stages;
s3, obtaining the oil property change condition of the clutch lubricating oil according to a temperature curve, wherein a change formula of temperature, dynamic viscosity and volume viscosity of the lubricating oil is as follows:
lglg(v+C)＝A+mlgT
v is the viscosity of the oil product at a temperature T (273+t ℃) in mm 2 S, A, C, m are constants;
s4, obtaining the influence of external parts of the clutch on clutch oil through dynamic simulation, and establishing a corresponding oil way according to the following conditions: the oil throwing and splashing effects promote the increase or decrease of the oil quantity, change of the motion state of oil particles, influence of positive pressure or negative pressure on the oil particles caused by the rotation direction and influence of oil return of a clutch on the oil quantity;
s5, oil stirring simulation is carried out in the whole gearbox environment through CFD fluid simulation software, and variables including the oil quantity, speed and position of lubricating oil produced by the clutch are counted due to the motion effect of external parts of the clutch, so that the parameters of the variables are parameterized;
s6, constructing a clutch fluid simulation model by utilizing CFD fluid simulation software, firstly inputting different oil product characteristic curves, which are obtained in the step S3 and are influenced by temperature, of the clutch in a sliding stage, a combining stage, a semi-separating stage and a fully separating stage, then establishing lubricating oil sources at corresponding positions under the same working condition according to the influence of external parts of the clutch on the oil quantity and the speed of the clutch in the step S5, reflecting the lubricating oil spraying to the clutch in a parameterized mode,
s7, analyzing and evaluating whether the calculation result meets the expected design index, when the calculation result does not meet the expected design index, carrying out optimal design on related components of the cooling system, and re-executing the steps S1-S5, and when the calculation result meets the expected design index, outputting the optimal design result to obtain oil mass data and lubrication cooling conditions of important parts focused by the clutch.
2. The wet clutch lubrication cooling simulation method according to claim 1, wherein: in the S1 step, the clutch internal parts comprise a return spring group, a friction plate, a pair of plates, a balance plate, a piston, a bearing, an inner bracket, a driven gear and an intermediate shaft.
3. A wet clutch lubrication cooling simulation method according to claim 1 or 2, wherein: in the step S4, the parameters of the external parts of the clutch comprise the rotational speed and the direction of the engine gear shaft and the differential gear shaft.
4. The wet clutch lubrication cooling simulation method according to claim 1, wherein: in the step S5, the grids of the following parts are refined: the inner and outer bracket holes, the friction plate pair gap, the intermediate shaft oil hole, the balance plate and the gap between the shafts.
5. The wet clutch lubrication cooling simulation method according to claim 1, wherein: in the step S5, parameters of oil product characteristics in four stages comprise temperature, dynamic viscosity, volume viscosity, tension coefficient and density.
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